Systems and methods for foam-based heat exchange during energy storage and recovery using compressed gas

ABSTRACT

In various embodiments, foam is compressed to store energy and/or expanded to recover energy.

RELATED APPLICATIONS

This application claims the benefit of and priority to U.S. ProvisionalPatent Application No. 61/486,937, filed May 17, 2011, U.S. ProvisionalPatent Application No. 61/489,762, filed May 25, 2011, U.S. ProvisionalPatent Application No. 61/512,981, filed Jul. 29, 2011, U.S. ProvisionalPatent Application No. 61/569,528, filed Dec. 12, 2011, U.S. ProvisionalPatent Application No. 61/601,641, filed Feb. 22, 2012, and U.S.Provisional Patent Application No. 61/620,018, filed Apr. 4, 2012. Theentire disclosure of each of these applications is hereby incorporatedherein by reference.

STATEMENT REGARDING FEDERALLY SPONSORED RESEARCH

This invention was made with government support under IIP-0923633awarded by the NSF and DE-OE0000231 awarded by the DOE. The governmenthas certain rights in the invention.

FIELD OF THE INVENTION

In various embodiments, the present invention relates to pneumatics,hydraulics, power generation, and energy storage, and more particularly,to systems and methods using pneumatic, pneumatic/hydraulic, and/orhydraulic cylinders for energy storage and recovery.

BACKGROUND

Storing energy in the form of compressed gas has a long history andcomponents tend to be well tested and reliable, and have long lifetimes.The general principle of compressed-gas or compressed-air energy storage(CAES) is that generated energy (e.g., electric energy) is used tocompress gas (e.g., air), thus converting the original energy topressure potential energy; this potential energy is later recovered in auseful form (e.g., converted back to electricity) via gas expansioncoupled to an appropriate mechanism. Advantages of compressed-gas energystorage include low specific-energy costs, long lifetime, lowmaintenance, reasonable energy density, and good reliability.

If a body of gas is at the same temperature as its environment, andexpansion occurs slowly relative to the rate of heat exchange betweenthe gas and its environment, then the gas will remain at approximatelyconstant temperature as it expands. This process is termed “isothermal”expansion. Isothermal expansion of a quantity of high-pressure gasstored at a given temperature recovers approximately three times morework than would “adiabatic expansion,” that is, expansion where no heatis exchanged between the gas and its environment—e.g., because theexpansion happens rapidly or in an insulated chamber. Gas may also becompressed isothermally or adiabatically.

An ideally isothermal energy-storage cycle of compression, storage, andexpansion would have 100% thermodynamic efficiency. An ideally adiabaticenergy-storage cycle would also have 100% thermodynamic efficiency, butthere are many practical disadvantages to the adiabatic approach. Theseinclude the production of higher temperature and pressure extremeswithin the system, heat loss during the storage period, and inability toexploit environmental (e.g., cogenerative) heat sources and sinks duringexpansion and compression, respectively. In an isothermal system, thecost of adding a heat-exchange system is traded against resolving thedifficulties of the adiabatic approach. In either case, mechanicalenergy from expanding gas must usually be converted to electrical energybefore use.

An efficient and novel design for storing energy in the form ofcompressed gas utilizing near isothermal gas compression and expansionhas been shown and described in U.S. Pat. No. 7,832,207, filed Apr. 9,2009 (the '207 patent) and U.S. Pat. No. 7,874,155, filed Feb. 25, 2010(the '155 patent), the disclosures of which are hereby incorporatedherein by reference in their entireties. The '207 and '155 patentsdisclose systems and techniques for expanding gas isothermally in stagedcylinders and intensifiers over a large pressure range in order togenerate electrical energy when required. Mechanical energy from theexpanding gas may be used to drive a hydraulic pump/motor subsystem thatproduces electricity. Systems and techniques for hydraulic-pneumaticpressure intensification that may be employed in systems and methodssuch as those disclosed in the '207 and '155 patents are shown anddescribed in U.S. Pat. No. 8,037,678, filed Sep. 10, 2010 (the '678patent), the disclosure of which is hereby incorporated herein byreference in its entirety.

In the systems disclosed in the '207 and '155 patents, reciprocalmechanical motion is produced during recovery of energy from storage byexpansion of gas in the cylinders. This reciprocal motion may beconverted to electricity by a variety of techniques, for example asdisclosed in the '678 patent as well as in U.S. Pat. No. 8,117,842,filed Feb. 14, 2011 (the '842 patent), the disclosure of which is herebyincorporated herein by reference in its entirety. The ability of suchsystems to either store energy (i.e., use energy to compress gas into astorage reservoir) or produce energy (i.e., expand gas from a storagereservoir to release energy) will be apparent to any person reasonablyfamiliar with the principles of electrical and pneumatic machines.

The power density (volumetric or mass-based) of an energy-storage systemthat approximates isothermal expansion and compression of a gas bymingling a heat-exchange liquid with the gas may be defined as themaximum sustained power (kilowatts, kW) that the system can eitherconvert to a stored form or extract from storage, divided by either thevolume (m³) or mass (kg) of the system. The power density (eithervolumetric or mass-based) of an energy-storage system therefore may haveunits of kW/m³ or of kW/kg. An energy-storage system having higher powerdensity will in general be capable of more economic storage andretrieval of energy than an otherwise comparable system with lower powerdensity, i.e., averaged over the lifetime of the system its use willrequire fewer cents per kilowatt-hour stored and retrieved (¢/kWh).

Power density may be increased by a number of techniques; one suchtechnique is to increase the rate at which thermal energy is exchangedby the heat-exchange liquid and the gas. One technique for achievingrapid heat exchange between the heat-exchange liquid and the gas is tospray the liquid through the gas as a mist or rain of droplets, whichtends to increase the surface area of a given volume of liquid comparedto the surface area of the same volume of liquid in a compact shape,e.g., a single cylinder or sphere. However, in many applications evenmore rapid heat exchange is desirable, and increasingly smallheat-exchange droplet size (i.e., for increased heat-exchange surfacearea) may be difficult or impractical to attain. Thus, there is a needfor systems and techniques for more-rapid heat exchange between aheat-exchange fluid and a gas to be or being compressed and/or expandedin compressed-gas energy storage and recovery systems.

SUMMARY

Embodiments of the present invention improve the performance of anenergy storage-and-recovery system that employs heat exchange between aliquid and a gas to approximate isothermal (constant-temperature)expansion and compression of the gas in cylinders by mingling the liquidand the gas to form an aqueous foam, which increases the surface area ofthe liquid and facilitates rapid heat exchange with the gas and,therefore, improved power density. Thermal energy is typically exchangedmore rapidly when liquid and gas are mingled as a foam than when the gasis brought into contact with liquid having a more compact shape (e.g., asingle cylinder) or divided into a number of bodies having a morecompact shape (e.g., spheroids, even if these are very small).Accelerated heat exchange is advantageous (e.g., supportive of highersystem power density) in energy storage-and-recovery systems thatapproximate isothermal expansion and compression of gas, as describedabove. Embodiments of the invention allow for characteristics of thefoam (e.g., bubble (i.e., “foam cell”) size, void fraction) to bealtered during operation of the system, offering advantages detailedhereinbelow. Herein, the void fraction of a foam (also termed “gasfraction”) of a foam is defined as the fraction of a given volume of thefoam that is occupied by gas.

An aqueous foam is a two-phase system (i.e., a system featuring both gasand liquid) in which a large volume fraction of gas is dispersed asbubbles or cells throughout a continuous liquid matrix (as discussed inJ. B. Winterburn and P. J. Martin, “Mechanisms of ultrasound foaminteractions,” Asia-Pac. J. Chem. Eng. 2009:4:184-190, the entiredisclosure of which is incorporated by reference herein). These gasbubbles are contained by liquid films typically stabilized by an admixedsurfactant, i.e., a substance consisting essentially of or comprisingsurface-active, amphiphilic molecules that preferentially accumulate atthe liquid-gas interface. These liquid films are typicallyinterconnected at their meeting points, forming a continuous liquidphase throughout the foam structure. The structure of a particular foamvaries depending on its liquid fraction; foams may be divided into twobroad classes accordingly. “Wet foams” consist essentially ofapproximately spherical bubbles separated by thick liquid films. In thelimit of perfectly spherical, close-packed gas bubbles in a wet foam,geometry determines that the void fraction in the foam is approximately0.74 by volume. Foams with void fractions greater than approximately0.74 are “dry foams,” in which polyhedral gas cells are separated bythin liquid lamellae (i.e., walls or membranes). Embodiments of thepresent invention utilize wet and/or dry aqueous foam.

In embodiments of the invention, a pneumatic compressor-expandercylinder (herein termed a “cylinder”) is divided into two chambers by aslidably disposed piston, at least one of which (herein termed the “airchamber”) may contain gas or a gas-liquid mixture (e.g., a foam). Gas tobe expanded or compressed may be introduced into the air chamber; aliquid (herein termed “heat-exchange liquid”) may also be introducedinto the air chamber. Force may be exerted on the piston by the fluidswithin the air chamber or by a rod aligned with the cylinder, passingthrough a suitable port in one end of the cylinder, and connected to amechanical device (e.g., crankshaft) external to the cylinder.

In one embodiment of the invention, liquid and gas are mingled to form afoam (i.e., the liquid and gas are “foamed”) in a chamber or vesselexternal to a cylinder in which gas is to be expanded or compressed. Inparticular, a liquid may be used that promotes foaming with air (oranother suitable gas) when agitated, sprayed, or otherwise energeticallymodified. An example of such a liquid is water containing, e.g., 2% to5% of certain additives (e.g., surfactants), some of which are describedin U.S. patent application Ser. No. 13/082,808, filed on Apr. 8, 2011(the '808 application), the entire disclosure of which is incorporatedby reference herein. The foam is admitted to the air chamber of thecylinder through a suitable mechanism (e.g., a valved port). Exchange ofthermal energy between the gas and the liquid occurs whenever the gasand liquid are in contact with each other, but occurs more rapidly whenfoaming has increased the surface area over which the gas and liquid arein contact with each other. In various states of operation, the airchamber of the cylinder may contain no foam, be partly filled with foam,or be substantially filled with foam.

In various embodiments of the invention, the chamber or vessel in whichthe liquid and gas are foamed is a storage reservoir for gas at highpressure (e.g., approximately 3,000 psi). Liquid tending to separatefrom the foam may accumulate at the bottom of the reservoir and may berecirculated into the reservoir through a spray head or otherfoam-generating mechanism in order to maintain or regenerate a quantityof foam within the storage reservoir.

In various embodiments of the invention, foam (or the separated liquidcomponent of a foam) that is at a desired temperature (e.g., relativelycold or relatively hot) may be diverted into a vessel in order to storeenergy therein. Herein, the energy of a system, e.g., the fluid contentsof a vessel, is the maximum amount of work that can ideally be performedby bringing the system into thermal equilibrium with the environment.Herein, a vessel in which relatively cool or hot liquid is stored forthe purpose of storing energy is termed a “thermal well.”

In various embodiments of the invention, the liquid and gas are foamedin a dedicated device, herein termed a “mixing chamber,” that may employspraying, eduction, sparging, passage through a packed bed or solidfoam, fogging, spray of suspended droplets, and/or other mechanisms toproduce foam. As utilized herein, a “sparger” is a mechanism for theintroduction of foam (typically a lower-liquid-content foam) and/or gasinto liquid and/or a foam (typically a higher liquid-content foam) toproduce foam therewith.

In various states of operation of certain embodiments, foam may bedirected to a vessel or chamber (e.g., placed in a fluid pathcommunicating between the storage reservoir and the mixing chamber, orbetween the air chamber of one cylinder and the air chamber of anothercylinder) for the purpose of separating the liquid and gas components ofthe foam. Such a vessel or chamber is herein termed a “separator.”Partial or substantially entire separation of foams may occur withinseparators, cylinders, mixing chambers, storage reservoirs, and othercomponents (e.g., tubing). Liquid separated from foam in a separator orother component may be passed through a heat exchanger to alter itstemperature, or otherwise treated or processed, and re-directed to thegeneration of foam in another portion of the system (e.g., a mixingchamber).

Fluid foams may be passed through one or more screens, riddles, or solidfoams (all of which are herein termed “screens”) to control foam quality(e.g., bubble uniformity, average bubble size). Such screens may beconstructed so as to permit alteration of bubble size in various statesof operation: for example, two perforated plates in substantial contactmay be caused to slide with respect to each other, aligning ordisaligning their perforations in a manner that allows passage ofvariously sized bubbles. Fluid foams may also be excited (e.g., in themixing chamber) with acoustic vibrations (e.g., ultrasound) in order toaffect the size and uniformity of the cells (bubbles) in the foam.

In various states of operation, gas or gas-liquid mixtures may bebypassed around a mixing chamber. For example, when gas is beingexpanded from storage, valves and piping may be configured so as to passthe gas through a mixing chamber for foaming. However, when gas is beingcompressed into storage, compressed gas or foam may be routed through abypass (e.g., a pipe), and not through the mixing chamber. Routing gasthrough a bypass will in general dissipate less energy than routingthrough a mixing chamber, and therefore improve system efficiency.

In various embodiments of the invention, alternatively or additionallyto foam generation outside a cylinder, foam may be generated by directinjection of liquid into the air chamber of a cylinder through, e.g., aspray head or other foam-generating device.

In various embodiments of the invention, foam may be excited withacoustic vibrations (e.g., ultrasound) in the air chamber of a cylinderto accelerate heat exchange between the gas and liquid components of thefoam. Acoustic vibrations may accelerate such heat exchange between thegas and liquid components of a foam through various mechanisms (e.g.,surface waves set up at the liquid-gas interfaces of bubbles or cells,or increased flow through lamellae and Plateau borders).

Various embodiments of the invention may include one or more of thefollowing components: mixing chambers, separators, bypasses, screens,ultrasound generators, assemblies of two or more cylinders operatingover different pressure ranges, and other components. As described inU.S. Pat. No. 7,802,426 (the '426 patent), the entire disclosure ofwhich is incorporated by reference herein, compressible fluid (e.g., gasor foam) undergoing either compression or expansion may be directed,continuously or in installments, through a heat-exchange subsystemexternal to the cylinder. The heat-exchange subsystem either rejectsheat to the environment (to cool fluid undergoing compression) orabsorbs heat from the environment (to warm fluid undergoing expansion).Again, an isothermal process may be approximated via judicious selectionof this heat-exchange rate.

Generally, the systems described herein may be operated in both anexpansion mode and in the reverse compression mode as part of afull-cycle energy storage system with high efficiency. For example, thesystems may be operated as both compressor and expander, storingelectricity in the form of the potential energy of compressed gas andproducing electricity from the potential energy of compressed gas.Alternatively, the systems may be operated independently as compressorsor expanders.

Embodiments of the present invention are typically utilized in energystorage systems utilizing compressed gas. In a compressed-gas energystorage system, gas is stored at high pressure (e.g., approximately3,000 psi). This gas may be expanded into a cylinder having a firstcompartment (or “chamber”) and a second compartment separated by apiston slidably disposed within the cylinder (or by another boundarymechanism). A shaft may be coupled to the piston and extend through thefirst compartment and/or the second compartment of the cylinder andbeyond an end cap of the cylinder, and a transmission mechanism may becoupled to the shaft for converting a reciprocal motion of the shaftinto a rotary motion, as described in the '678 and '842 patents.Moreover, a motor/generator may be coupled to the transmissionmechanism. Alternatively or additionally, the shaft of the cylinders maybe coupled to one or more linear generators, as described in the '842patent.

As also described in the '842 patent, the range of forces produced byexpanding a given quantity of gas in a given time may be reduced throughthe addition of multiple, series-connected cylinder stages. That is, asgas from a high-pressure reservoir is expanded in one chamber of afirst, high-pressure cylinder, gas from the other chamber of the firstcylinder is directed to the expansion chamber of a second,lower-pressure cylinder. Gas from the lower-pressure chamber of thissecond cylinder may either be vented to the environment or directed tothe expansion chamber of a third cylinder operating at still lowerpressure; the third cylinder may be similarly connected to a fourthcylinder; and so on.

The principle may be extended to more than two cylinders to suitparticular applications. For example, a narrower output force range fora given range of reservoir pressures is achieved by having a first,high-pressure cylinder operating between, for example, approximately3,000 psig and approximately 300 psig and a second, larger-volume,lower-pressure cylinder operating between, for example, approximately300 psig and approximately 30 psig. When two expansion cylinders areused, the range of pressure within either cylinder (and thus the rangeof force produced by either cylinder) is reduced as the square rootrelative to the range of pressure (or force) experienced with a singleexpansion cylinder, e.g., from approximately 100:1 to approximately 10:1(as set forth in the '842 patent). Furthermore, as set forth in the '678patent, N appropriately sized cylinders can reduce an original operatingpressure range R to R^(1/N). Any group of N cylinders staged in thismanner, where N≧2, is herein termed a cylinder group.

Embodiments of the present invention provide for the use ofpositive-displacement pumps to efficiently circulate liquid atrelatively high pressure, e.g., liquid for the production of liquidsprays and/or aqueous foams used to approximate isothermal expansion andcompression within cylinder assemblies, with resulting gain in theefficiency of the overall energy-storage and energy-recovery processes.Such positive-displacement pumps may be piston-in-tube-type pumps,rotary positive-displacement pumps (e.g., screw pumps, progressivecavity pumps), or other types of pump. As disclosed in U.S. patentapplication Ser. No. 13/009,409, filed Jan. 19, 2011 (the '409application), the entire disclosure of which is incorporated byreference herein, efficient circulation of high-pressure fluid may beachieved using a high-inlet pressure low-differential pressure pump suchas a reciprocating, double-acting, positive-displacement pump having afluid-filled chamber containing a piston or other mechanism thatseparates the fluid on one side of the piston from the fluid on theother side; or using a screw pump, progressive cavity pump, or otherrotary positive-displacement pump.

Various embodiments of the present invention use a rotarypositive-displacement pump (e.g., screw pump) to enable theenergy-efficient pumping of fluid already at high pressure (e.g., fromapproximately 1,000 pounds per square inch gauge [psig] to approximately3,000 psig, or higher) to a somewhat higher pressure (e.g.,approximately 50 psig higher than the input pressure). Usefulapplications of such a pump include, but are not limited to, (1) theintroduction of a foam, foaming liquid, or liquid spray into a vesselstoring pressurized gas, the resulting foam or spray enabling thetransfer of heat to or from the gas, (2) the energy-efficientintroduction of a foam, foaming liquid, or liquid spray into a chambercontaining pressurized gas, where the foam, foaming liquid, or sprayenables the approximately isothermal expansion or compression of the gaswithin the chamber.

Herein, a screw pump is a positive-displacement pump that employs one ormore screws in order to compress a fluid; a “positive displacement pump”is any device that traps a volume of fluid and then moves (displaces)that fluid, possibly compressing it in so doing; and a “screw” is a rodwith a helical ridge or thread running along its length. Typically, in ascrew pump, a screw meshes with a complementary surface defined by oneor more ancillary components (e.g., a housing, or one or more otherscrews) in such a way that one or more approximately spiral-shapedvolumes of fluid are trapped between the surface of the screw and thecomplementary surface. As the screw revolves, fluid is admitted at oneend of the screw, trapped in approximately spiral-shaped volumes, movedlongitudinally along the screw while possibly undergoing compression,and expelled or exhausted at the other end of the screw. In screw pumpswhere the pitch of the screw changes longitudinally, the volumes offluid trapped between the screw and the complementary surface arecompressed as they move longitudinally along the screw. Screw pumps thatcompress fluid are typically termed screw compressors. Screw pumps andcompressors of various designs, including single-screw, dual-screw, andtriple-screw pumps, as well as the properties and features of such pumpsand compressors, will be known to persons reasonably familiar with theprinciples of compressors and pumps. Herein, the term “screw pump”generally refers to a screw compressor of the dual- or triple-screwtype, but the use of screw pumps or rotary positive-displacement pumpsof other types, including but not limited to Wendelkolben pumps, helicaltwisted Roots pumps, and eccentric screw pumps, is also contemplated andwithin the scope of the invention.

It will be apparent to persons familiar with the principles ofcompressors and pumps that a screw pump capable of compressing fluidmay, in principle, be operated in reverse as an expander. In suchreverse operation, fluid at a relatively high pressure is admitted atone end of the turning screw, trapped in an approximately spiral-shapedvolume between the screw and the complementary surface, and movedlongitudinally along the rotating screw as the trapped volume expands.This fluid, at lower pressure than the pressure at which it wasadmitted, is exhausted from the end of the screw opposite to the end atwhich it was admitted.

Embodiments of the present invention also provide for increasing theminimum or starting pressure within the inlet chambers of the cylindergroup in compression mode by a pre-compressor. As disclosed in U.S. Pat.No. 8,104,274, filed May 18, 2011 (the '274 patent), the entiredisclosure of which is incorporated by reference herein, pre-compressionof air prior to the inlet chambers of the cylinder group may be used toincrease power density of a compressed-gas energy storage system.Additionally, venting of gas from the cylinder group at pressures aboveatmospheric may increase power density. At least some of this potentialenergy remaining in the vented super-atmospheric pressure gas may berecovered in an expander device. In various embodiments where startingpressure is increased by a pre-compressor, the pre-compressor mayinclude or consist essentially of a rotodynamic blower (e.g., radialcentrifugal, axial) or positive-displacement type blower (e.g.,lobe-type) or pump (e.g., screw pump). In various embodiments wherecylinder group venting pressure is super-atmospheric, an expander mayinclude or consist essentially of a second unidirectional device or thesame device as the pre-compressor operated bidirectionally. Examples ofsuch devices that may be used as expanders include rotodynamic expanders(e.g., radial centrifugal, axial) and positive-displacement typeexpanders (e.g., piston-type) and pump/motors (e.g. screw pump/motor).

When, e.g., a screw pump is operated as a pre-compressor, work isperformed to compress the fluid passing through the pump. This energy issupplied by a mechanism exterior to the pump (e.g., an electric motor).When, e.g., a screw pump is operated as an expander, the gas performswork on the pump and on any mechanisms to which the pump is attached(e.g., an electric generator). Moreover, compression of gas within ascrew pump operated as a compressor (or within any other pre-compressorwith sufficient capacity to avoid complete destruction (i.e.,separation) of the foam prior to compression) may be made to occursubstantially isothermally by the introduction, at and/or before theintake of the screw pump, and/or within the screw pump itself, of a foamor foaming liquid that partially or substantially fills the trappedspiral-shaped volume of fluid within the screw pump during thecompression of the gas. The foaming liquid may be combined with gasprior to undergoing compression in order to produce substantiallyisothermal compression of the gas. Similarly, expansion of gas within ascrew pump operated as an expander (or within any other expander withsufficient capacity to avoid complete destruction of the foam prior toexpansion) may be made to occur substantially isothermally by theintroduction, at and/or before the intake of the screw pump, and/orwithin the screw pump itself, of a suitable quantity of a foam orfoaming liquid that partially or substantially fills the trappedspiral-shaped volume of fluid within the screw pump during the expansionof the gas. Droplets of heat-exchange liquid (introduced through, e.g.,perforations in the surface of the screw or in the complementarysurface) may be combined with foam or employed instead of foam in orderto effect substantially isothermal compression or expansion of gaswithin the screw pump. In a pump used as a pre-compressor or as apost-expander, substantially isothermal operation may increase theoverall efficiency of the energy storage system.

Increasing the minimum or starting pressure within the inlet chamber ofa cylinder group typically decreases the range of gauge pressuresoccurring within the cylinder group (and thus the range of forcesexerted by the cylinder group). Gauge pressure range is reduced indirect proportion to degree of pre-compression. For example, for asystem having a non-pre-compressed inlet pressure of approximately 1psig and a maximum pressure of approximately 2,500 psig, the range ofgauge pressures is approximately 2500:1; for an otherwise identicalsystem having a pre-compressed inlet pressure of approximately 5 psigand a maximum pressure of approximately 2,500 psig, the range of gaugepressures is one-fifth as great (i.e., approximately 500:1).

Additionally, the mass of air in the inlet chamber at the initialpressure is increased in a pre-compressed system versus anon-pre-compressed system by approximately the ratio of the absolutepressures (e.g., approximately 19.7 psia/14.7 psia, depending on thepolytropic coefficient of the compression or expansion). Thus, if asingle compression stroke takes the same amount of time in a system withpre-compression as in a system without pre-compression, a greater massof compressed air at the output pressure (e.g., approximately 2,500psig), representing a proportionately greater amount of stored energy,is produced in a given time interval. In other words, for a singlecomplete compression by a given cylinder, higher compression power isachieved by pre-compression.

It will be apparent to persons familiar with the principles ofcompressors and pumps that some blowers and pumps (e.g., screw pump) maybe operated in reverse as an expanders. That is, e.g., fluid at arelatively high pressure is admitted at one end of the turning screw,trapped in an approximately spiral-shaped volume between the screw andthe complementary surface, and moved longitudinally along the rotatingscrew as the trapped volume expands. This gas, at lower pressure thanthe pressure at which it was admitted, is exhausted from the end of thescrew opposite to the end at which it was admitted. Expansion of gaswithin a screw pump that is operated as an expander may be made to occursubstantially isothermally by the introduction, at and/or before theintake of the screw pump, and/or within the screw pump itself, of a foamor foaming liquid that partially or substantially fills the trappedspiral-shaped volume of fluid within the screw pump during the expansionof the gas.

It will be clear to persons familiar with the principles of compressorsand pumps that by similar reasoning, when the system is operated as anexpander rather than as a compressor, higher expansion power is achievedby allowing the outlet pressure of the cylinder group to besignificantly above atmospheric pressure. Moreover, expanding thissuper-atmospheric-pressure outlet gas through a device upon which thegas performs work (e.g., a screw-pump expander) allows some of thepotential energy of the outlet gas to be converted into work. Recoveryof this work increases the overall efficiency of the energy storagesystem.

Every compression or expansion of a quantity of gas, where such acompression or expansion is herein termed “a gas process,” is generallyone of three types: (1) adiabatic, during which the gas exchanges noheat with its environment and, consequently, rises or falls intemperature, (2) isothermal, during which the gas exchanges heat withits environment in such a way as to remain at constant temperature, and(3) polytropic, during which the gas exchanges heat with its environmentbut its temperature does not remain constant. Perfectly adiabatic gasprocesses are not practical because some heat is always exchangedbetween any body of gas and its environment (ideal insulators andreflectors do not exist); perfectly isothermal gas processes are notpractical because for heat to flow between a quantity of gas and aportion of its environment (e.g., a body of liquid), a nonzerotemperature difference must exist between the gas and itsenvironment—e.g., the gas must be allowed to heat during compression inorder that heat may be conducted to the liquid. Hence real-world gasprocesses are typically polytropic, though they may approximateadiabatic or isothermal processes.

The Ideal Gas Law states that for a given quantity of gas having mass m,pressure p, volume V, and temperature T, pV=mRT, where R is the gasconstant (R=287 J/K•kg for air). For an isothermal process, T is aconstant throughout the process, so pV=C, where C is some constant.

For a polytropic process, as will be clear to persons familiar with thescience of thermodynamics, pV^(n)=C throughout the process, where n,termed the polytropic index, is some constant generally between 1.0 and1.6. For n=1, pV^(n)=pV¹=pV=C, i.e., the process is isothermal. Ingeneral, a process for which n is close to 1 (e.g., 1.05) may be deemedapproximately isothermal.

For an adiabatic process, pV^(n)=C, where γ, termed the adiabaticcoefficient, is equal to the ratio of the gas's heat capacity atconstant pressure C_(P) to its heat capacity at constant volume, C_(v),i.e., γ=C_(p)/C_(v). In practice, γ is dependent on pressure. For air,the adiabatic coefficient γ is typically between 1.4 and 1.6.

Herein, we define a “substantially isothermal” gas process as one havingn≦1.1. The gas processes conducted within cylinders described herein arepreferably substantially isothermal with n≦1.05. Herein, wherever a gasprocess taking place within a cylinder assembly or storage vessel isdescribed as “isothermal,” this word is synonymous with the term“substantially isothermal.”

The amount of work done in compression or expansion of a given quantityof gas varies substantially with polytropic index n. For compressions,the lowest amount of work done is for an isothermal process and thehighest for an adiabatic process, and vice versa for expansions. Hence,for gas processes such as typically occur in the compressed-gas energystorage systems described herein, the end temperatures attained byadiabatic, isothermal, and substantially isothermal gas processes aresufficiently different to have practical impact on the operability andefficiency of such systems. Similarly, the thermal efficiencies ofadiabatic, isothermal, and substantially isothermal gas processes aresufficiently different to have practical impact on the overallefficiency of such energy storage systems. For example, for compressionof a quantity of gas from initial temperature of 20° C. and initialpressure of 0 psig (atmospheric) to a final pressure of 180 psig, thefinal temperature T of the gas will be exactly 20° C. for an isothermalprocess, approximately 295° C. for an adiabatic process, approximately95° C. for a polytropic compression having polytropic index n=1.1 (10%increase in n over isothermal case of n=1), and approximately 60° C. fora polytropic compression having polytropic index n=1.05 (5% increase inn over isothermal case of n=1). In another example, for compression of1.6 kg of air from an initial temperature of 20° C. and initial pressureof 0 psig (atmospheric) to a final pressure of approximately 180 psig,including compressing the gas into a storage reservoir at 180 psig,isothermal compression requires approximately 355 kilojoules of work,adiabatic compression requires approximately 520 kilojoules of work, anda polytropic compression having polytropic index n=1.045 requiresapproximately 375 kilojoules of work; that is, the polytropiccompression requires approximately 5% more work than the isothermalprocess, and the adiabatic process requires approximately 46% more workthan the isothermal process.

It is possible to estimate the polytropic index n of gas processesoccurring in cylinder assemblies such as are described herein byempirically fitting n to the equation pV^(n)=C, where pressure p andvolume V of gas during a compression or expansion, e.g., within acylinder, may both be measured as functions of time from pistonposition, known device dimensions, and pressure-transducer measurements.Moreover, by the Ideal Gas Law, temperature within the cylinder may beestimated from p and V, as an alternative to direct measurement by atransducer (e.g., thermocouple, resistance thermal detector, thermistor)located within the cylinder and in contact with its fluid contents. Inmany cases, an indirect measurement of temperature via volume andpressure may be more rapid and more representative of the entire volumethan a slower point measurement from a temperature transducer. Thus,temperature measurements and monitoring described herein may beperformed directly via one or more transducers, or indirectly asdescribed above, and a “temperature sensor” may be one of such one ormore transducers and/or one or more sensors for the indirect measurementof temperature, e.g., volume, pressure, and/or piston-position sensors.

All of the approaches described above for converting potential energy ina compressed gas into mechanical and electrical energy may, ifappropriately designed, be operated in reverse to store electricalenergy as potential energy in a compressed gas. Since the accuracy ofthis statement will be apparent to any person reasonably familiar withthe principles of electrical machines, power electronics, pneumatics,and the principles of thermodynamics, the operation of these mechanismsto both store energy and recover it from storage will not be describedfor each embodiment. Such operation is, however, contemplated and withinthe scope of the invention and may be straightforwardly realized withoutundue experimentation.

The systems described herein, and/or other embodiments employingfoam-based heat exchange, liquid-spray heat exchange, and/or externalgas heat exchange, may draw or deliver thermal energy via theirheat-exchange mechanisms to external systems (not shown) for purposes ofcogeneration, as described in U.S. Pat. No. 7,958,731, filed Jan. 20,2010 (the '731 patent), the entire disclosure of which is incorporatedby reference herein.

The compressed-air energy storage and recovery systems described hereinare preferably “open-air” systems, i.e., systems that take in air fromthe ambient atmosphere for compression and vent air back to the ambientatmosphere after expansion, rather than systems that compress and expanda captured volume of gas in a sealed container (i.e., “closed-air”systems). The systems described herein generally feature one or morecylinder assemblies for the storage and recovery of energy viacompression and expansion of gas. The systems also include (i) areservoir for storage of compressed gas after compression and supply ofcompressed gas for expansion thereof, and (ii) a vent for exhaustingexpanded gas to atmosphere after expansion and supply of gas forcompression. The storage reservoir may include or consist essentiallyof, e.g., one or more one or more pressure vessels (i.e., containers forcompressed gas that may have rigid exteriors or may be inflatable, thatmay be formed of various suitable materials such as metal or plastic,and that may or may not fall within ASME regulations for pressurevessels), pipes (i.e., rigid containers for compressed gas that may alsofunction as and/or be rated as fluid conduits, have lengths well inexcess (e.g., >100×) of their diameters, and do not fall within ASMEregulations for pressure vessels), or caverns (i.e., naturally occurringor artificially created cavities that are typically locatedunderground). Open-air systems typically provide superior energy densityrelative to closed-air systems.

Furthermore, the systems described herein may be advantageously utilizedto harness and recover sources of renewable energy, e.g., wind and solarenergy. For example, energy stored during compression of the gas mayoriginate from an intermittent renewable energy source of, e.g., wind orsolar energy, and energy may be recovered via expansion of the gas whenthe intermittent renewable energy source is nonfunctional (i.e., eithernot producing harnessable energy or producing energy atlower-than-nominal levels). As such, the systems described herein may beconnected to, e.g., solar panels or wind turbines, in order to store therenewable energy generated by such systems.

In one aspect, embodiments of the invention feature a method ofrecovering energy. A first foam having a first foam expansion ratio istransferred to a first cylinder assembly, and the first foam is expandedin the first cylinder assembly, thereby recovering energy therefrom.Thereafter, a second foam is transferred to a second cylinder assemblydifferent from the first cylinder assembly. The second foam has a secondfoam expansion ratio larger than the first foam expansion ratio. Thesecond foam is expanded in the second cylinder assembly, therebyrecovering energy therefrom. The first and second cylinder assembliesare preferably portions of a single power unit utilized for theexpansion (and possibly compression) of gas and/or foam.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The expanded second foam maybe exhausted from the second cylinder assembly. At least a gaseousportion of the expanded second foam may be exhausted to ambientatmosphere. After expanding the first foam, the expanded first foam maybe exhausted from the first cylinder assembly. The second foam mayinclude or consist essentially of at least a portion (e.g., a gaseousportion or a foam portion) of the expanded first foam. The expandedfirst foam may be exhausted into a foam vessel, and heat-transfer liquidmay be introduced into the foam vessel to form the second foam. Afterexpanding the first foam, at least a portion of the expanded first foammay be separated into gaseous and liquid components. The separation mayinclude or consist essentially of mechanical separation (e.g., by one ormore blades, one or more shears, one or more baffles, and/or one or morecentrifuges) and/or application of ultrasound energy. The second foammay be formed by introducing heat-transfer liquid into the gaseouscomponent of the expanded first foam. The liquid component of theexpanded first foam may be stored (e.g., in a storage reservoir). Themass ratio of the first foam may be approximately equal to the massratio of the second foam. The average cell size and/or the uniformity ofcell size of the first foam may be altered before expanding the firstfoam. The average cell size and/or the uniformity of cell size of thesecond foam may be altered before expanding the second foam. The foammass ratio of the first foam and/or the second foam may be selected fromthe range of 1 to 4. The first foam and/or the second foam may beexpanded substantially isothermally. The first foam may be formed bymingling heat-transfer liquid and compressed gas. The void fraction ofthe first foam may be controlled by controlling a rate of transfer ofheat-transfer liquid into the compressed gas. A pressure or atemperature within the first cylinder assembly may be sensed, and therate of transfer may be controlled in response to the sensed pressureand/or temperature. Expanding the first foam and expanding the secondfoam may both drive a crankshaft mechanically coupled to the first andsecond cylinder assemblies.

In another aspect, embodiments of the invention feature a method ofstoring energy. Heat-transfer liquid is dispersed into gas (e.g., air atapproximately atmospheric pressure) to form a first foam having a firstfoam expansion ratio. The first foam is compressed within a firstcylinder assembly. Thereafter, a second foam is transferred to a secondcylinder assembly different from the first cylinder assembly. The secondfoam has a second foam expansion ratio smaller than the first foamexpansion ratio. The second foam is compressed within the secondcylinder assembly, and the compressed second foam is exhausted from thesecond cylinder assembly. At least the gaseous component of thecompressed second foam is stored (e.g., in a storage reservoir).

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The first foam may betransferred to the first cylinder assembly prior to compressing thefirst foam within the first cylinder assembly. At least a portion of aliquid component may be separated from the compressed second foam priorto storing the gaseous component. The separation may include or consistessentially of mechanical separation (e.g., by one or more blades, oneor more shears, one or more baffles, and/or one or more centrifuges)and/or application of ultrasound energy. Both the gaseous component andthe liquid component of the compressed second foam may be stored (i.e.,together in the same storage reservoir or separately in separatereservoirs). After compressing the first foam within the first cylinderassembly, the compressed first foam may be exhausted from the firstcylinder assembly. The second foam may include or consist essentially ofat least a portion (e.g., a gaseous portion or a foam portion) of thecompressed first foam. The compressed first foam may be exhausted into afoam vessel (e.g., a pressure vessel, a pipe, or a manifold).Heat-transfer liquid may be introduced into the foam vessel to form thesecond foam. After compressing the first foam, at least a portion of thecompressed first foam may be separated into gaseous and liquidcomponents. The separation may include or consist essentially ofmechanical separation (e.g., by one or more blades, one or more shears,one or more baffles, and/or one or more centrifuges) and/or applicationof ultrasound energy. The second foam may be formed by introducingheat-transfer liquid into the gaseous component of the compressed firstfoam. The heat-transfer liquid introduced into the gaseous component ofthe compressed first foam may include or consist essentially of at leasta portion of the liquid component of the separated compressed firstfoam. The liquid component of the compressed first foam may be stored(e.g., in a storage reservoir). The mass ratio of the first foam may beapproximately equal to the mass ratio of the second foam. The averagecell size and/or the uniformity of cell size of the first foam may bealtered before compressing the first foam. The average cell size and/orthe uniformity of cell size of the second foam may be altered beforecompressing the second foam. The foam mass ratio of the first foamand/or of the second foam may be selected from the range of 1 to 4. Thefirst foam and/or the second foam may be compressed substantiallyisothermally. The void fraction of the first foam may be controlled bycontrolling a rate of dispersal of heat-transfer liquid into the gas. Apressure or a temperature within the first cylinder assembly may besensed, and the rate of dispersal may be controlled in response to thesensed pressure and/or temperature. A crankshaft may be driven tocompress the first foam and the second foam. The crankshaft may bemechanically coupled to the first and second cylinder assemblies.Forming the first foam may include or consist essentially of sprayingheat-transfer liquid on a screen.

In yet another aspect, embodiments of the invention feature an energystorage and recovery system. The system includes a cylinder assembly forstoring energy by compression and/or recovering energy by expansion, astorage reservoir, and a mixing chamber for (i) receiving gas andheat-transfer liquid from the storage reservoir, (ii) mixing the gaswith the heat-transfer liquid to form a foam, and (iii) transferring thefoam to the cylinder assembly. The mixing chamber is selectively fluidlyconnected to the cylinder assembly and the storage reservoir. The mixingchamber is selectively fluidly connected to the storage reservoir by afirst conduit for transferring gas (and which may additionally transferliquid, but is typically connected to a substantially gas-filled regionof the storage reservoir) and a second conduit, different from the firstconduit, for transferring heat-transfer liquid (and which mayadditionally transfer gas, but is typically connected to a substantiallyliquid-filled region of the storage reservoir).

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The mixing chamber mayinclude a mechanism for altering at least one characteristic of the foam(e.g., foam cell size and/or foam cell size uniformity). The mechanismmay include or consist essentially of a screen and/or a source ofultrasound energy. A foam-generating mechanism may be coupled to thefirst conduit and/or the second conduit in the mixing chamber. Thefoam-generating mechanism may include or consist essentially of one ormore nozzles, a rotating blade, a source of ultrasound energy, and/or asparger. The system may include a second cylinder assembly storingenergy by compression or recovering energy by expansion over a pressurerange different from a pressure range of the cylinder assembly. A ventfor exhausting expanded gas to atmosphere may be selectively fluidlyconnected to the second cylinder assembly. A control system may controlthe cylinder assembly and/or the mixing chamber to enforce substantiallyisothermal compression and/or substantially isothermal expansion in thecylinder assembly. A sensor may detect pressure within the cylinderassembly and/or the mixing chamber, and the control system may beresponsive to the sensor. The control system may control the flow rateof heat-transfer liquid into the mixing chamber in response to thedetected pressure. A circulation apparatus (e.g., a variable-speed pump)may transfer heat-transfer liquid within the second conduit. A movableboundary mechanism may separate the cylinder assembly into two chambers.A crankshaft may be mechanically coupled to the boundary mechanism andmay convert reciprocal motion of the boundary mechanism into rotarymotion. A motor/generator may be coupled to the crankshaft. The storagereservoir may include or consist essentially of a pressure vessel, apipe, and/or a cavern.

In an additional aspect, embodiments of the invention feature a methodof energy storage. Foam is compressed within a cylinder to a firstpressure. The compressed foam is transferred to a storage reservoir,where it at least partially separates into gaseous and liquid componentsat approximately the first pressure. At least a portion of the liquidcomponent is removed from the storage reservoir and stored at a secondpressure lower than the first pressure.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. Prior to storing the atleast a portion of the liquid component at the second pressure, energymay be recovered from the at least a portion of the liquid component byreducing its pressure. A crankshaft may be driven with the recoveredenergy. The crankshaft may be mechanically coupled to the cylinder.Prior to compressing the foam, the foam may be formed by minglingheat-transfer liquid and gas. The foam may be formed in a foam vesselselectively fluidly connected to the cylinder. The foam vessel mayinclude or consist essentially of a pressure vessel, a pipe, and/or amanifold. Forming the foam may include or consist essentially ofspraying heat-transfer liquid on a screen. Prior to compressing thefoam, the average cell size or the uniformity of cell size of the foammay be altered. The void fraction of the foam may be controlled bycontrolling the rate of transfer of heat-transfer liquid into the gas. Apressure and/or a temperature within the cylinder may be sensed, and therate of transfer may be controlled in response thereto. At least aportion of the stored liquid component may be mingled with gas to formadditional foam, which may then be compressed. The foam mass ratio ofthe foam may be selected from the range of 1 to 4. The foam may becompressed substantially isothermally. Compressing the foam may includeor consist essentially of driving a crankshaft coupled to the cylinder.The compressed foam may at least partially separate due to gravity. Thecompressed foam may be at least partially separated via at mechanicalseparation (e.g., by a blade, a shear, a baffle, and/or a centrifuge)and/or application of ultrasound energy.

In another aspect, embodiments of the invention feature an energystorage and recovery system including first and second cylinderassemblies for storing energy by compression and/or recovering energy byexpansion. The second cylinder assembly has a pressure range ofoperation different from a pressure range of operation of the firstcylinder assembly. A first foam vessel for at least one of intermediatestorage or formation of a first foam therein is selectively fluidlyconnected to the first cylinder assembly. A second foam vessel for atleast one of intermediate storage or formation of a second foam thereinis selectively fluidly connected to the first cylinder assembly and tothe second cylinder assembly. A third foam vessel for at least one ofintermediate storage or formation of a third foam therein is selectivelyfluidly connected to the second cylinder assembly.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. A vent to a surroundingatmosphere may be selectively fluidly connected to the third foamvessel. A storage reservoir for the storage of compressed gas (e.g., asa gas or as part of a foam) may be selectively fluidly connected to thefirst foam vessel. The system may include a recirculation mechanism fortransferring foam and/or liquid from a first location in the first foamvessel to a second location in the first foam vessel different from thefirst location. The first foam vessel may include or consist essentiallyof at least one of a pressure vessel, a pipe, or a manifold. The secondfoam vessel may include or consist essentially of at least one of apressure vessel, a pipe, or a manifold. The third foam vessel mayinclude or consist essentially of at least one of a pressure vessel, apipe, or a manifold.

In yet another aspect, embodiments of the invention feature an energystorage and recovery system including or consisting essentially of afoam-generating mechanism, a manifold, and, selectively fluidlyconnected to the manifold, at least one cylinder assembly expansionand/or compression of foam therewithin. The foam-generating mechanismincludes or consists essentially of a spray chamber, at least onedispersal mechanism for dispersing liquid into gas flowing through thespray chamber, and fluidly coupled to the at least one dispersalmechanism, a reservoir for containing the liquid. The manifold receivesfoam from the spray chamber.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. A circulation mechanism(e.g., a fan) may at least partially form a flow of gas through thespray chamber. Another circulation mechanism (e.g., a pump such as avariable-speed pump) may circulate liquid from the reservoir to the atleast one dispersal mechanism. A valve for exhausting gas from themanifold at least during formation of foam within the manifold may beconnected to the manifold. A screen through which foam is formed in themanifold from the dispersed liquid in the spray chamber may be disposedbetween the spray chamber and the manifold. A separation chamber may beselectively fluidly connected to the manifold. The separation chambermay comprise therewithin a separation mechanism for separating foam intogaseous and liquid components. The separation chamber may be selectivelyfluidly connected to the reservoir. The separation mechanism may includeor consist essentially of a source of ultrasound energy, a blade, ashear, a baffle, and/or a centrifuge.

In an aspect, embodiments of the invention feature an energy storage andrecovery system including or consisting essentially of a plurality ofcylinder pairs, a first foam-generating mechanism for generating foam ata low pressure within a first pressure range, and a secondfoam-generating mechanism, different from the first foam-generatingmechanism, for generating foam at a high pressure within a secondpressure range. Each cylinder pair includes or consists essentially of(i) a low-pressure cylinder for expansion and/or compression over thefirst pressure range and (ii) a high-pressure cylinder for expansionand/or compression over the second pressure range, which is differentfrom the first pressure range and overlaps the first pressure range atleast at an intermediate pressure.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. A manifold for intermediatestorage of foam at the low pressure may be selectively fluidly connectedto (i) the plurality of low-pressure cylinders and (ii) the firstfoam-generating mechanism. A manifold for intermediate storage of foamat the high pressure may be selectively fluidly connected to (i) theplurality of high-pressure cylinders and (ii) the second foam-generatingmechanism. The first foam-generating mechanism may include or consistessentially of (i) at least one dispersal mechanism for dispersingliquid into gas and (ii) a screen through which foam is formed from thedispersed liquid. The second foam-generating mechanism may include orconsist essentially of a dispersal mechanism for at least one ofspraying, sparging, fogging, or agitating liquid. The system may includea third foam-generating mechanism for generating foam at theintermediate pressure. A manifold for intermediate storage of foam atthe intermediate pressure may be selectively fluidly connected to (i)the plurality of low-pressure cylinders, (ii) the plurality ofhigh-pressure cylinders, and (iii) the third foam-generating mechanism.

In another aspect, embodiments of the invention feature an energystorage and recovery system including or consisting essentially of acylinder assembly for compression to store energy and/or expansion torecover energy, a foam-generating mechanism for introducing a foamwithin the cylinder assembly, a pumping cylinder for pumpingheat-transfer fluid to the foam-generating mechanism, a first storagereservoir for storage of compressed gas, and a second storage reservoirfor storage of heat-transfer fluid. The cylinder assembly includes afirst movable boundary mechanism therein and a first rod coupled to thefirst movable boundary mechanism. The pumping cylinder includes a secondmovable boundary mechanism therein and a second rod coupled to thesecond movable boundary mechanism. The first storage reservoir isselectively fluidly connected to the cylinder assembly. The secondstorage reservoir is selectively fluidly connected to the pumpingcylinder.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The first storage reservoirand the second storage reservoir may be the same reservoir or may bedifferent (i.e., discrete) reservoirs. A heat-transfer subsystem maythermally condition the heat-transfer fluid, and may include or consistessentially of a heat exchanger. The first and second rods may bemechanically coupled to a mechanism for interconverting reciprocalmotion of the first and second rods with rotary motion. The mechanismmay include or consist essentially of a crankshaft. The crankshaft maymaintain the first and second rods in a fixed phase relationship. Thefoam-generating mechanism may be disposed within the cylinder assemblyor disposed outside of the cylinder assembly and connected thereto via aconduit. The foam-generating mechanism may include or consistessentially of one or more nozzles, a rotating blade, a source ofultrasound energy, and/or a sparger. The first storage reservoir maystore fluid at a pressure different from a pressure at which the secondstorage reservoir stores fluid.

In an additional aspect, embodiments of the invention feature a methodof storing and recovering energy. Compressed gas is transferred from astorage reservoir to a mixing chamber selectively fluidly connectedthereto. In the mixing chamber, a first foam including or consistingessentially of the compressed gas and a heat-transfer fluid is formed.The first foam is transferred from the mixing chamber to a cylinder. Thefirst foam is expanded in the cylinder to recover energy therefrom. Theexpanded first foam is removed from the cylinder. A second foam isintroduced into the cylinder and compressed in the cylinder to storeenergy therein. At least a portion of the compressed second foam istransferred to the storage reservoir, the transfer bypassing the mixingchamber.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The average cell size and/orthe uniformity of cell size of the first foam may be altered beforeexpanding the first foam. Removing the expanded first foam from thecylinder may include or consist essentially of exhausting a gaseouscomponent of the expanded first foam to ambient atmosphere. Removing theexpanded first foam from the cylinder may include or consist essentiallyof transferring the expanded first foam to a second cylinder, where itmay be further expanded. The expanded first foam may be separated into agaseous component and a liquid component. The expanded first foam may beseparated via mechanical separation (e.g., by a blade, a shear, abaffle, and/or a centrifuge) and/or application of ultrasound energy.The liquid component of the expanded first foam may be stored. The foammass ratio of the first foam may be selected from the range of 1 to 4.Transferring at least a portion of the compressed second foam to thestorage reservoir may include or consist essentially of transferring agaseous component of the at least a portion of the compressed secondfoam to the storage reservoir. Transferring at least a portion of thecompressed second foam to the storage reservoir may include or consistessentially of transferring both a gaseous component and a liquidcomponent of the at least a portion of the compressed second foam to thestorage reservoir. The at least a portion of the compressed second foammay be transferred to the storage reservoir via a bypass connectionbetween the cylinder and the storage reservoir. A valve maysubstantially prevent entry of the compressed second foam into themixing chamber during transfer to the storage reservoir. A secondportion of the compressed second foam may be transferred from thecylinder to the storage reservoir via the mixing chamber. The first foamand/or the second foam is expanded substantially isothermally. Thecylinder may include a piston therein, and expanding the first foam inthe cylinder may drive (i) a mechanism mechanically coupled to thepiston and/or (ii) a hydraulic system coupled to the cylinder. Expandingthe first foam may drive the mechanism, and the mechanism may include orconsist essentially of a crankshaft. Forming the first foam may includeor consist essentially of transferring heat-transfer liquid into themixing chamber. The void fraction of the first foam may be controlled bycontrolling the rate of transfer of the heat-transfer liquid into themixing chamber. A pressure and/or a temperature within the cylinderand/or the mixing chamber may be sensed, and the rate of transfer may becontrolled in response thereto.

In yet another aspect, embodiments of the invention feature a method ofrecovering energy. A first foam including or consisting essentially of acompressed gas and a heat-transfer fluid is formed within a storagereservoir and transferred to a cylinder. The first foam is expanded inthe cylinder to recover energy therefrom, and the expanded first foam isremoved from the cylinder. A second foam is compressed in the cylinderto store energy therein, and at least a portion of the compressed secondfoam is stored in the storage reservoir.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. Forming the first foam mayinclude or consist essentially of, within the storage reservoir, mixingheat-transfer fluid and compressed gas via a foam-generating mechanism.The foam-generating mechanism may include or consist essentially of oneor more nozzles, a rotating blade, a source of ultrasound energy, and/ora sparger. Heat-transfer liquid (e.g., substantially non-foamedheat-transfer liquid) may be circulated from a region of the storagereservoir to the foam-generating mechanism. The heat-transfer liquid maybe circulated outside of the storage reservoir. The average cell sizeand/or the uniformity of cell size of the first foam may be alteredbefore expanding the first foam. Removing the expanded first foam fromthe cylinder may include or consist essentially of exhausting a gaseouscomponent of the expanded first foam to ambient atmosphere. The expandedfirst foam may be separated into a gaseous component and a liquidcomponent. The expanded first foam may be separated via mechanicalseparation (e.g., by a blade, a shear, a baffle, and/or a centrifuge)and/or application of ultrasound energy. The liquid component of theexpanded first foam may be stored (e.g., in the storage reservoir). Thefoam mass ratio of the first foam may be selected from the range of 1 to4. Storing at least a portion of the compressed second foam in thestorage reservoir may include or consist essentially of storing agaseous component of the at least a portion of the compressed secondfoam. Storing at least a portion of the compressed second foam in thestorage reservoir may include or consist essentially of storing both agaseous component and a liquid component of the at least a portion ofthe compressed second foam. Removing the expanded first foam from thecylinder may include or consist essentially of transferring the expandedfirst foam to a second cylinder, where it may be further expanded. Thefirst foam and/or the second foam may be expanded substantiallyisothermally. The cylinder may include a piston therein. Expanding thefirst foam in the cylinder may drive (i) a mechanism mechanicallycoupled to the piston (e.g., a crankshaft) and/or (ii) a hydraulicsystem coupled to the cylinder.

In an additional aspect, embodiments of the invention feature a methodof storing and recovering energy. Gas is transferred into a cylinder.Heat-transfer liquid is transferred into the cylinder to therein mixwith the gas and form a foam including or consisting essentially of thegas and the heat-transfer liquid. Within the cylinder, the foam iscompressed to store energy and/or expanded to recover energy, and thecompressed or expanded foam is exhausted from the cylinder.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. Gas may be transferred intothe cylinder from a storage reservoir, and the heat-transfer liquid maybe transferred into the cylinder from the storage reservoir. The gas andthe heat-transfer liquid may be transferred into the cylinder viadifferent inlets. The foam may be compressed, and at least a portion ofthe compressed foam may be stored within a storage reservoir. Storing atleast a portion of the compressed foam within the storage reservoir mayinclude or consist essentially of storing a gaseous component of thecompressed foam. Storing at least a portion of the compressed foamwithin the storage reservoir may include or consist essentially ofstoring both a gaseous component and a liquid component of thecompressed foam. The void fraction of the foam may be controlled bycontrolling a rate of transfer of the heat-transfer liquid into thecylinder. A pressure and/or a temperature within the cylinder may besensed, and the rate of transfer may be controlled in response thereto.The foam may be expanded, and exhausting the expanded foam from thecylinder may include or consist essentially of exhausting a gaseouscomponent of the expanded foam to ambient atmosphere. The foam may beexpanded, and exhausting the expanded foam from the cylinder may includeor consist essentially of transferring the expanded foam to a secondcylinder, where it may be further expanded. The foam may be expanded,and the expanded foam may be separated into a gaseous component and aliquid component. The expanded foam may be separated via mechanicalseparation (e.g., by a blade, a shear, a baffle, and/or a centrifuge)and/or application of ultrasound energy. The foam may be expanded, andthe liquid component of the expanded foam may be stored. The foam massratio of the foam may be selected from the range of 1 to 4. The foam maybe expanded or compressed substantially isothermally. The foam may beexpanded and the cylinder may include a piston therein. Expanding thefoam may drive (i) a mechanism mechanically coupled to the piston (e.g.,a crankshaft) and/or (ii) a hydraulic system coupled to the cylinder.

In yet an additional aspect, embodiments of the invention feature amethod of storing and recovering energy. A gas is compressed or expandedin a plurality of discrete stages, each stage being performed over adifferent pressure range. During one of the stages, heat is exchangedbetween the gas and discrete droplets of a first heat-transfer fluidintroduced into the gas. During another one of the stages, heat isexchanged between the gas and a second heat-transfer fluid, the gas andthe second heat-transfer fluid being combined to form a foam.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. After the compression orexpansion during the another one of the stages, at least a portion ofthe foam may be separated into gaseous and liquid components. The atleast a portion of the foam may be separated via mechanical separation(e.g., by a blade, a shear, a baffle, and/or a centrifuge) and/orapplication of ultrasound energy. The gas may be compressed, and,thereafter, stored in a storage reservoir. The gas may be expanded, and,thereafter, vented to ambient atmosphere. The first and secondheat-transfer fluids may include the same liquid (e.g., water). Thesecond heat-transfer fluid may include a foaming additive. The discretedroplets of the first heat-transfer fluid may be introduced into the gasby spraying. The heat exchange between the discrete droplets of thefirst heat-transfer fluid and the gas may render the expansion orcompression during that stage substantially isothermal. The heatexchange within the foam between the gas and the second heat-transferfluid may render the expansion or compression during that stagesubstantially isothermal. The expansion or compression of foam may beperformed within a cylinder. The foam may be generated by mixing the gaswith the second heat-transfer fluid within the cylinder. The foam may begenerated by mixing the gas with the second heat-transfer fluid outsideof the cylinder, and then the foam may be transferred into the cylinder.The average cell size and/or the uniformity of cell size of the foam maybe altered before the foam enters the cylinder. The gas may be expanded,and the cylinder may include a piston therein. Expanding the gas in thecylinder may drive (i) a mechanism mechanically coupled to the piston(e.g., a crankshaft) and/or (ii) a hydraulic system coupled to thecylinder. The foam mass ratio of the foam may be selected from the rangeof 1 to 4. Forming the foam may include or consist essentially oftransferring the second heat-transfer fluid into the gas. The voidfraction of the foam may be controlled by controlling a rate of transferof the second heat-transfer fluid. A pressure and/or a temperaturewithin at least one of the stages may be sensed, and the rate oftransfer may be controlled in response thereto.

In an aspect, embodiments of the invention feature a method of storingand recovering energy. Two different processes are performed within acylinder, the processes comprising (i) compressing gas to store energyand (ii) expanding gas to recover energy. During one of the processes,heat is exchanged with the gas by introducing discrete droplets of afirst heat-transfer fluid thereto. During the other one of theprocesses, heat is exchanged with the gas by mixing the gas with asecond heat-transfer fluid to form a foam.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. After the other one of theprocesses, at least a portion of the foam may be separated into gaseousand liquid components. The separation may be performed via mechanicalseparation (e.g., by a blade, a shear, a baffle, and/or a centrifuge)and/or application of ultrasound energy. After gas is compressed, it maybe stored in a storage reservoir. After gas is expanded, it may bevented to ambient atmosphere. The first and second heat-transfer fluidsmay include the same liquid (e.g., water). The second heat-transferfluid may include a foaming additive. The discrete droplets of the firstheat-transfer fluid may be introduced into the gas by spraying. The heatexchange between the discrete droplets of the first heat-transfer fluidand the gas may render that process substantially isothermal. The heatexchange within the foam between the gas and the second heat-transferfluid may render that process substantially isothermal. The foam may beformed by mixing the gas with the second heat-transfer fluid within thecylinder. The foam may be formed by mixing the gas with the secondheat-transfer fluid outside of the cylinder, and then the foam may betransferred into the cylinder. The average cell size and/or theuniformity of cell size of the foam may be altered before the foamenters the cylinder. The cylinder may include a piston therein.Expanding the gas in the cylinder may drive (i) a mechanism mechanicallycoupled to the piston (e.g., a crankshaft) or (ii) a hydraulic systemcoupled to the cylinder. The foam mass ratio of the foam may be selectedfrom the range of 1 to 4. The void fraction of the foam may becontrolled by controlling the rate of transfer of the secondheat-transfer fluid into the gas. A pressure and/or a temperature of thegas may be sensed, and the rate of transfer may be controlled inresponse thereto.

In another aspect, embodiments of the invention feature an energystorage and recovery system including or consisting essentially of acylinder assembly storing energy by compression and/or recovering energyby expansion, a storage reservoir, a mixing chamber, and a bypassconduit. The storage reservoir is selectively fluidly connected to thecylinder assembly. The mixing chamber is selectively fluidly connectedto the cylinder assembly and the storage reservoir, and the mixingchamber (i) receives gas from the storage reservoir, (ii) mixes the gaswith a heat-transfer liquid to form a foam, and (iii) transfers the foamto the cylinder assembly. The bypass conduit selectively fluidlyconnects the cylinder assembly directly to the storage reservoir andtransfers gas and/or foam from the cylinder assembly to the storagereservoir without traversing the mixing chamber.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The mixing chamber may beselectively fluidly connected to the storage reservoir by (i) a firstconduit for transferring gas and (ii) a second conduit, different fromthe first conduit, for transferring heat-transfer liquid. A mechanismfor altering at least one characteristic of the foam (e.g., foam cellsize and/or foam cell size uniformity) may be disposed in the mixingchamber. The mechanism may include or consist essentially of a screenand/or a source of ultrasound energy. A foam-generating mechanism may bedisposed in the mixing chamber. The foam-generating mechanism mayinclude or consist essentially of one or more nozzles, a rotating blade,a source of ultrasound energy, and/or a sparger. The system may includea second cylinder assembly for storing energy by compression orrecovering energy by expansion over a pressure range different from apressure range of the cylinder assembly. A vent for exhausting expandedgas to atmosphere may be selectively fluidly connected to the secondcylinder assembly. The system may include a control system forcontrolling the cylinder assembly and/or the mixing chamber to enforcesubstantially isothermal compression and/or substantially isothermalexpansion in the cylinder assembly. The system may include a sensor fordetecting a pressure within the cylinder assembly and/or the mixingchamber, and the control system may be responsive to the sensor. Thecontrol system may control the flow rate of heat-transfer liquid intothe mixing chamber in response to the detected pressure. A circulationapparatus (e.g., a pump such as a variable-speed pump) may transferheat-transfer liquid to the mixing chamber. A movable boundary mechanismmay separate the cylinder assembly into two chambers. A crankshaft forconverting reciprocal motion of the boundary mechanism into rotarymotion may be mechanically coupled to the boundary mechanism. Amotor/generator may be coupled to the crankshaft. The storage reservoirmay include or consist essentially of a pressure vessel, a pipe, and/ora cavern.

In yet another aspect, embodiments of the invention feature an energystorage and recovery system including or consisting essentially of acylinder assembly storing energy by compression and/or recovering energyby expansion, a storage reservoir selectively fluidly connected to thecylinder assembly, and a foam-generating mechanism for generating,within the storage reservoir, a foam including or consisting essentiallyof gas and a heat-transfer liquid.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. A mechanism for altering atleast one characteristic of the foam (e.g., foam cell size and/or foamcell size uniformity) may be disposed between the storage reservoir andthe cylinder assembly. The mechanism may include or consist essentiallyof a screen and/or a source of ultrasound energy. The foam-generatingmechanism may include or consist essentially of one or more nozzles, arotating blade, a source of ultrasound energy, and/or a sparger. Thesystem may include a second cylinder assembly for storing energy bycompression or recovering energy by expansion over a pressure rangedifferent from a pressure range of the cylinder assembly. A vent forexhausting expanded gas to atmosphere may be selectively fluidlyconnected to the second cylinder assembly. The system may include acontrol system for controlling the cylinder assembly to enforcesubstantially isothermal compression and/or substantially isothermalexpansion therein. The system may include a sensor for detectingpressure or temperature within the cylinder assembly, and the controlsystem may be responsive to the sensor. A circulation apparatus (e.g., apump such as a variable-speed pump) may transfer heat-transfer liquid tothe foam generating mechanism. A conduit may selectively fluidly connecta bottom region of the storage reservoir with the foam-generatingmechanism. The conduit may extend outside of the storage reservoir. Amovable boundary mechanism may separate the cylinder assembly into twochambers. A crankshaft for converting reciprocal motion of the boundarymechanism into rotary motion may be mechanically coupled to the boundarymechanism. A motor/generator may be coupled to the crankshaft. Thestorage reservoir may include or consist essentially of a pressurevessel, a pipe, and/or a cavern.

In an additional aspect, embodiments of the invention feature an energystorage and recovery system including or consisting essentially of acylinder assembly for storing energy by compression and/or recoveringenergy by expansion, a storage reservoir, and disposed within thecylinder assembly, a foam-generating mechanism for generating a foam viaintroduction of a heat-transfer liquid into gas within the cylinderassembly. The cylinder assembly is selectively fluidly connected to thestorage reservoir by (i) a first conduit for transferring gas and (ii) asecond conduit, different from the first conduit, for transferringheat-transfer liquid to the foam-generating mechanism.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The foam-generatingmechanism may include or consist essentially of one or more nozzles, arotating blade, a source of ultrasound energy, and/or a sparger. Thesystem may include a second cylinder assembly for at least one ofstoring energy by compression or recovering energy by expansion over apressure range different from a pressure range of the cylinder assembly.A vent for exhausting expanded gas to atmosphere may be selectivelyfluidly connected to the second cylinder assembly. The system mayinclude a control system for controlling the cylinder assembly toenforce substantially isothermal compression and/or substantiallyisothermal expansion therein. The system may include a sensor fordetecting a pressure or a temperature within the cylinder assembly, andthe control system may be responsive to the sensor. The control systemmay control a flow rate of heat-transfer liquid through thefoam-generating mechanism in response to the detected pressure. Acirculation apparatus (e.g., a pump such as a variable-speed pump) maytransfer heat-transfer liquid within the second conduit. A movableboundary mechanism may separate the cylinder assembly into two chambers.A crankshaft for converting reciprocal motion of the boundary mechanisminto rotary motion may be mechanically coupled to the boundarymechanism. A motor/generator may be coupled to the crankshaft. Thestorage reservoir may include or consist essentially of a pressurevessel, a pipe, and/or a cavern.

In an aspect, embodiments of the invention feature an energy storage andrecovery system including or consisting essentially of a cylinderassembly for storing energy by compression and/or recovering energy byexpansion, a spray mechanism for introducing discrete droplets of afirst heat-transfer liquid within the cylinder assembly for heatexchange between gas and the discrete droplets of the firstheat-transfer liquid, and, discrete from the spray mechanism, afoam-generating mechanism for generating and/or introducing within thecylinder assembly a foam including or consisting essentially of gas anda second heat-transfer liquid.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The first and secondheat-transfer liquids may include the same liquid (e.g., water). Thesecond heat-transfer liquid may include a foaming additive. The spraymechanism may include or consist essentially of a spray head and/or aspray rod. The foam-generating mechanism may include or consistessentially of one or more nozzles, a rotating blade, a source ofultrasound energy, and/or a sparger. A storage reservoir for storage ofcompressed gas (e.g., a pressure vessel, a pipe, and/or a cavern) may beselectively fluidly connected to the cylinder assembly. A vent forexhausting expanded gas to ambient atmosphere may be selectively fluidlyconnected to the cylinder assembly.

In another aspect, embodiments of the invention feature an energystorage and recovery system including or consisting essentially of (i) aplurality of cylinder assemblies for, each over a different pressurerange, storing energy by compression and/or recovering energy byexpansion, (ii) selectively fluidly connected to one of the cylinderassemblies, a spray mechanism for introducing therein discrete dropletsof a first heat-transfer liquid, and (iii) selectively fluidly connectedto a different one of the cylinder assemblies, a foam-generatingmechanism for generating and/or introducing therewithin a foam includingor consisting essentially of gas and a second heat-transfer liquid.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The first and secondheat-transfer liquids may include the same liquid (e.g., water). Thesecond heat-transfer liquid may include a foaming additive. The spraymechanism may include or consist essentially of a spray head and/or aspray rod. The foam-generating mechanism may include or consistessentially of one or more nozzles, a rotating blade, a source ofultrasound energy, and/or a sparger. A storage reservoir for storage ofcompressed gas (e.g., a pressure vessel, a pipe, and/or a cavern) may beselectively fluidly connected to the cylinder assembly. A vent forexhausting expanded gas to ambient atmosphere may be selectively fluidlyconnected to the cylinder assembly.

In yet another aspect, embodiments of the invention feature a method ofenergy recovery. A piston within a pumping cylinder is driven totransfer heat-transfer liquid therefrom to a foam-generating mechanism.Compressed gas is transferred to a cylinder assembly or to thefoam-generating mechanism. Via the foam-generating mechanism, (i) a foamis formed by mingling the heat-transfer liquid with the compressed gasand (ii) the foam is introduced within the cylinder assembly. The foamis expanded within the cylinder assembly, the expansion driving a pistonwithin the cylinder assembly. At least a portion of the expanded foam isexhausted from the cylinder assembly.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The compressed gas may betransferred to the cylinder assembly from a first storage reservoir.Heat-transfer liquid may be transferred to the pumping cylinder from asecond storage reservoir. The first and second storage reservoirs may bethe same reservoir. At least a portion of the expanded foam may beseparated into gaseous and liquid components. The liquid component maybe transferred to the first storage reservoir. The separation may beperformed via mechanical separation (e.g., by a blade, a shear, abaffle, and/or a centrifuge) and/or application of ultrasound energy.The second storage reservoir may be separate and distinct from the firststorage reservoir. The storage pressure within the first storagereservoir may be higher than the storage pressure within the secondstorage reservoir (which may be, e.g., approximately atmosphericpressure). At least a portion of the expanded foam may be separated intogaseous and liquid components. The liquid component may be transferredto the second storage reservoir. The separation may be performed viamechanical separation (e.g., by a blade, a shear, a baffle, and/or acentrifuge) and/or application of ultrasound energy. The heat-transferliquid may be thermally conditioned (i.e., heated or cooled) prior tothe heat-transfer liquid entering the foam-generating mechanism. Thefoam-generating mechanism may be disposed within the cylinder assembly.The foam-generating mechanism may be disposed outside the cylinderassembly and connected thereto by a conduit. The pistons within thepumping cylinder and the cylinder assembly may be driven simultaneously.At least a portion of the expanded foam may be separated into gaseousand liquid components. The separation may be performed via mechanicalseparation (e.g., by a blade, a shear, a baffle, and/or a centrifuge)and/or application of ultrasound energy. Exhausting at least a portionof the expanded foam from the cylinder assembly may include or consistessentially of exhausting a gaseous portion of the expanded foam toambient atmosphere. Exhausting at least a portion of the expanded foamfrom the cylinder assembly may include or consist essentially oftransferring the expanded foam or a gaseous portion thereof to a secondcylinder assembly for further expansion thereof. The foam mass ratio ofthe foam may be selected from the range of 1 to 4. The void fraction ofthe foam may be controlled by controlling a rate of transfer of theheat-transfer liquid to the foam-generating mechanism. A pressure and/ora temperature within the cylinder and/or the foam-generating mechanismmay be sensed, and the rate of transfer may be controlled in responsethereto.

In an additional aspect, embodiments of the invention feature a methodof energy storage. A piston within a pumping cylinder is driven totransfer heat-transfer liquid therefrom to a foam-generating mechanism.Gas is transferred to a cylinder assembly or to the foam-generatingmechanism. Via the foam-generating mechanism, (i) a foam is formed bymingling the heat-transfer liquid with the compressed gas and (ii) thefoam is introduced within the cylinder assembly. A piston within thecylinder assembly is driven to compress the foam within the cylinderassembly. At least a portion of the compressed foam is exhausted fromthe cylinder assembly.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. Exhausting the at least aportion of the compressed foam from the cylinder assembly may include orconsist essentially of transferring the compressed foam to a firststorage reservoir. Exhausting the at least a portion of the compressedfoam from the cylinder assembly may include or consist essentially oftransferring a gaseous component of the compressed foam to a firststorage reservoir. Exhausting the at least a portion of the compressedfoam from the cylinder assembly may include or consist essentially oftransferring a liquid component of the compressed foam to a secondstorage reservoir. The first and second storage reservoirs may be thesame reservoir. The second storage reservoir may be separate anddistinct from the first storage reservoir. The storage pressure withinthe first storage reservoir may be higher than the storage pressurewithin the second storage reservoir (which may be, e.g., approximatelyatmospheric pressure). The heat-transfer liquid may be thermallyconditioned (i.e., heated or cooled) prior to the heat-transfer liquidentering the foam-generating mechanism. The foam-generating mechanismmay be disposed within the cylinder assembly. The foam-generatingmechanism may be disposed outside the cylinder assembly and connectedthereto by a conduit. The pistons within the pumping cylinder and thecylinder assembly may be driven simultaneously. At least a portion ofthe compressed foam may be separated into gaseous and liquid components.The separation may be performed via mechanical separation (e.g., by ablade, a shear, a baffle, and/or a centrifuge) and/or application ofultrasound energy. Gas may be transferred to the cylinder assembly or tothe foam-generating mechanism from ambient atmosphere. Gas may betransferred to the cylinder assembly or to the foam-generating mechanismfrom a second cylinder assembly after compression of the gas within thesecond cylinder assembly. The foam mass ratio of the foam may beselected from the range of 1 to 4. The void fraction of the foam may becontrolled by controlling a rate of transfer of the heat-transfer liquidto the foam-generating mechanism. A pressure and/or a temperature withinthe cylinder and/or the foam-generating mechanism may be sensed, and therate of transfer may be controlled in response thereto.

In an aspect, embodiments of the invention feature an energy storage andrecovery system including or consisting essentially of a first cylinderassembly for at least one of compression to store energy or expansion torecover energy and a second cylinder assembly for at least one ofcompression to store energy or expansion to recover energy. The firstcylinder assembly includes or consists essentially of (i) a firstcylinder, (ii) at least partially disposed within the first cylinder, afirst pumping mechanism for circulating heat-transfer fluid from thefirst cylinder, and (iii) a first foam-generating mechanism for minglingheat-transfer fluid with gas to form a foam and introducing the foamwithin the first cylinder. The second cylinder assembly includes orconsists essentially of (i) a second cylinder, (ii) at least partiallydisposed within the second cylinder and selectively fluidly connected tothe first foam-generating mechanism, a second pumping mechanism forcirculating heat-transfer fluid from the second cylinder, and (iii) asecond foam-generating mechanism for mingling heat-transfer fluid withgas to form a foam and introducing the foam within the second cylinder,the second foam-generating mechanism being selectively fluidly connectedto the first pumping mechanism.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The first pumping mechanismmay include or consist essentially of a first piston disposed within thefirst cylinder and separating the first cylinder into two compartments,a first piston rod comprising a first cavity and coupled to the firstpiston, and a first hollow tube disposed at least partially in the firstcavity and extending through at least a portion of the first cylinder.Relative motion between the first hollow tube and the first piston rodmay circulate heat-transfer fluid into and out of the first cavity. Thesecond pumping mechanism may include or consist essentially of a secondpiston disposed within the second cylinder and separating the secondcylinder into two compartments, a second piston rod comprising a firstcavity and coupled to the second piston, and a second hollow tubedisposed at least partially in the second cavity and extending throughat least a portion of the second cylinder. Relative motion between thesecond hollow tube and the second piston rod may circulate heat-transferfluid into and out of the second cavity. The first and second pistonrods may be mechanically coupled to a common crankshaft. A firstheat-exchange subsystem may thermally condition heat-transfer fluidcirculating to the first foam-generating mechanism. The firstheat-exchange subsystem may include or consist essentially of a heatexchanger. The first heat-exchange subsystem may be fluidly connected tothe first foam-generating mechanism and the second pumping mechanism. Asecond heat-exchange subsystem may thermally condition heat-transferfluid circulating to the second foam-generating mechanism. The secondheat-exchange subsystem may include or consist essentially of a heatexchanger. The second heat-exchange subsystem may be fluidly connectedto the second foam-generating mechanism and the first pumping mechanism.A first storage reservoir for storage of gas and/or heat-transfer fluidmay be selectively fluidly connected to the first and second cylinderassemblies. A second storage reservoir for storage of gas and/orheat-transfer fluid may be selectively fluidly connected to the firstand second cylinder assemblies. The storage pressure of the firststorage reservoir may be higher than the storage pressure of the secondstorage reservoir (which may be approximately atmospheric pressure). Thefirst and/or second storage reservoirs may be selectively fluidlyconnected to the first and/or second pumping mechanisms. The firstfoam-generating mechanism may be disposed within the first cylinder. Thefirst foam-generating mechanism may be disposed outside of the firstcylinder and connected thereto via a conduit. The second foam-generatingmechanism may be disposed within the second cylinder. The secondfoam-generating mechanism may be disposed outside of the second cylinderand connected thereto via a conduit. The first foam-generating mechanismmay include or consist essentially of one or more nozzles, a rotatingblade, a source of ultrasound energy, and/or a sparger. The secondfoam-generating mechanism may include or consist essentially of one ormore nozzles, a rotating blade, a source of ultrasound energy, and/or asparger.

In another aspect, embodiments of the invention feature a method ofenergy recovery utilizing an energy-recovery system including orconsisting essentially of (i) a first cylinder assembly comprising afirst cylinder, a first pumping mechanism, and a first foam-generatingmechanism and (ii) a second cylinder assembly comprising a secondcylinder, a second pumping mechanism, and a second foam-generatingmechanism. An expansion stroke is performed with the first cylinderassembly and an exhaust stroke is performed with the second cylinderassembly. The expansion stroke includes or consists essentially of (i)mingling heat-transfer fluid and gas at the first foam-generatingmechanism to form a foam, (ii) expanding the foam within the firstcylinder, and (iii) introducing heat-transfer fluid into the firstpumping mechanism. The exhaust stroke includes or consists essentiallyof (i) exhausting foam or a gaseous component thereof from the secondcylinder and (ii) pumping heat-transfer fluid with the second pumpingmechanism to the first foam-generating mechanism.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The exhaust stroke mayinclude or consist essentially of thermally conditioning (e.g., heating)the heat-transfer fluid pumped with the second pumping mechanism beforeit enters the first foam-generating mechanism. An expansion stroke maybe performed with the second cylinder assembly, and an exhaust strokemay be performed with the first cylinder assembly. The expansion strokemay include or consist essentially of (i) mingling heat-transfer fluidand gas at the second foam-generating mechanism to form a second foam,(ii) expanding the second foam within the second cylinder, and (iii)introducing heat-transfer fluid into the second pumping mechanism. Theexhaust stroke may include or consist essentially of (i) exhausting foamor a gaseous component thereof from the first cylinder and (ii) pumpingheat-transfer fluid with the first pumping mechanism to the secondfoam-generating mechanism.

In yet another aspect, embodiments of the invention feature a method ofenergy storage utilizing an energy-recovery system including orconsisting essentially of (i) a first cylinder assembly comprising afirst cylinder, a first pumping mechanism, and a first foam-generatingmechanism and (ii) a second cylinder assembly comprising a secondcylinder, a second pumping mechanism, and a second foam-generatingmechanism. A compression stroke is performed with the first cylinderassembly. The compression stroke includes or consists essentially of (i)within the first cylinder, compressing a foam generated by the firstfoam-generating mechanism, and (ii) pumping heat-transfer fluid with thefirst pumping mechanism to the second foam-generating mechanism. Acompression stroke is performed with the second cylinder assembly. Thecompression stroke includes or consists essentially of (i) within thesecond cylinder, compressing a second foam generated by the secondfoam-generating mechanism, and (ii) pumping heat-transfer fluid with thesecond pumping mechanism to the first foam-generating mechanism.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. An intake stroke may beperformed with the first cylinder assembly. The intake stroke mayinclude or consist essentially of (i) receiving gas within the firstcylinder and (ii) introducing heat-transfer fluid into the first pumpingmechanism. An intake stroke may be performed with the second cylinderassembly. The intake stroke may include or consist essentially of (i)receiving gas within the second cylinder and (ii) introducingheat-transfer fluid into the second pumping mechanism. The compressionstroke of the first cylinder assembly may include thermally conditioning(e.g., cooling) the heat-transfer fluid pumped with the first pumpingmechanism before it enters the second foam-generating mechanism. Thecompression stroke of the second cylinder assembly may include thermallyconditioning (e.g., cooling) the heat-transfer fluid pumped with thesecond pumping mechanism before it enters the first foam-generatingmechanism.

In an additional aspect, embodiments of the invention feature a systemfor efficient power demand response. The system includes or consistsessentially of (i) a first energy-storage system for supplying power inresponse to demand up to a first power-demand level, (ii) connected tothe first energy-storage system, a second energy-storage system forsupplying power in response to demand greater than the firstpower-demand level, and (iii) a heat-exchange subsystem for thermallyconditioning at least a portion of the first and/or secondenergy-storage systems, thereby increasing a collective efficiency ofthe first and second energy-storage systems.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The first energy-storagesystem may include or consist essentially of a battery, a flywheel,and/or an ultracapacitor. The second energy-storage system may includeor consist essentially of a compressed-gas energy-storage system thatsupplies power by expanding compressed gas (e.g., in the form of afoam). The first and second energy-storage systems may be connected inparallel to a power grid. The first power-demand level may beapproximately 500 kW. The heat-exchange subsystem may recover thermalenergy from the first energy-storage system for thermally conditioning,in the second energy-storage system, (i) heat-transfer fluid forthermally conditioning gas undergoing expansion and/or compression orfor mingling with gas to form foam, (ii) gas or foam undergoingexpansion and/or compression, and/or (iii) gas or foam stored in astorage reservoir prior to expansion. The heat-exchange subsystem mayinclude or consist essentially of a first heat exchanger associated withthe first energy-storage system and a second heat exchanger associatedwith the second energy-storage system that is (i) separate from thefirst heat exchanger and (ii) selectively fluidly connectable to thefirst heat exchanger. The first heat exchanger may be fluidly connectedto a first radiator and/or a first thermal well and the second heatexchanger may be fluidly connected to a second radiator and/or a secondthermal well.

In yet an additional aspect, embodiments of the invention feature amethod of power delivery. A time-varying power-demand level is detected.Power is supplied from a first energy-storage system when thepower-demand level is less than or equal to a threshold level. Power issupplied from a second energy-storage system when the power-demand levelis greater than the threshold level. At least a portion of the firstand/or second energy-storage systems is thermally conditioned (i.e.,heated or cooled), thereby increasing a collective efficiency of thefirst and second energy-storage systems.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. Power may be supplied fromthe first energy-storage system only when the power-demand level is lessthan or equal to the threshold level. Power may be supplied from thesecond energy-storage system only when the power-demand level is greaterthan the threshold level. Thermally conditioning may include or consistessentially of recovering thermal energy from the first energy-storagesystem and thermally conditioning at least a portion of the secondenergy-storage system with the recovered thermal energy. Thermallyconditioning the at least a portion of the second energy-storage systemmay include or consist essentially of thermally conditioning (i)heat-transfer fluid for thermally conditioning gas undergoing expansionand/or compression or for mingling with gas to form foam, (ii) gas orfoam undergoing expansion and/or compression, and/or (iii) gas or foamstored in a compressed-gas reservoir prior to expansion. Power may besupplied from the first and second energy-storage systems over a commonbus line. Supplying power from the second energy-storage system mayinclude or consist essentially of expanding gas and/or foam to recoverenergy therefrom.

In an aspect, embodiments of the invention feature a method of energystorage and recovery utilizing a power unit comprising a cylinderassembly for the compression of gas to store energy and/or the expansionof gas to recover energy. Gas is compressed in the power unit.Heat-transfer liquid from a thermal well is introduced into the gasprior to and/or during compression, the heat-transfer liquid absorbingthermal energy from the gas during compression. At least a portion ofthe heat-transfer liquid is transferred back to the thermal well tostore the thermal energy therein. Thereafter, gas is expanded in thepower unit. Heat-transfer liquid from the thermal well is introducedinto the gas prior to and/or during expansion, the gas absorbing thermalenergy from the heat-transfer liquid during expansion.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The heat-transfer liquid maybe introduced into the gas by spraying the heat-transfer liquid into thegas. Introducing the heat-transfer liquid into the gas may form a foamcomprising the heat-transfer liquid and the gas. At least a portion ofthe foam may be separated into gas and heat-transfer liquid prior totransferring the at least a portion of the heat-transfer liquid back tothe thermal well. Introducing the heat-transfer liquid prior to and/orduring compression may render the compression substantially isothermal.Introducing the heat-transfer liquid prior to and/or during expansionmay render the expansion substantially isothermal. Waste thermal energyproduced by the power unit may be stored in the thermal well. Thermalenergy may be exchanged between the thermal well and the surroundingenvironment. Thermal energy may be exchanged between the thermal welland the surrounding environment while the power unit is neithercompressing nor expanding. The temperature of the heat-transfer liquidintroduced into the gas prior to and/or during compression may be belowambient temperature. The temperature of the heat-transfer liquidintroduced into the gas prior to and/-or during expansion may be aboveambient temperature. Compressed gas may be stored after compression, andstored compressed gas may be expanded during expansion. Storingcompressed gas may include storing heat-transfer fluid at an elevatedtemperature. The stored heat-transfer fluid may be transferred to thethermal well, thereby storing thermal energy therein. Expanded gas maybe vented to atmosphere after expansion.

In another aspect, embodiments of the invention feature an energystorage and recovery system configured for use with a thermal well forcontaining heat-transfer fluid therein. The system includes or consistsessentially of (i) a power unit comprising a cylinder assembly for,therewithin, compression of gas to store energy and/or expansion of gasto recover energy, (ii) a mechanism for introducing heat-transfer liquidinto the gas prior to and/or during the compression and/or expansion,the mechanism configured for selective fluid connection to the thermalwell, (iii) a conduit for selectively transferring heat-transfer liquidintroduced into the gas back into the thermal well, and (iv) thermallyconnected to the power unit and the thermal well, a waste-heatheat-exchange system for transferring waste thermal energy from thepower unit to the thermal well.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The system may include anenvironmental heat-exchange system configured for thermal connection tothe thermal well and the surrounding environment. The system may includea control system for (i) sensing an operating state of the power unitand (ii) operating the environmental heat-exchange system only when thepower unit is neither expanding nor compressing gas. A reservoir forstorage of compressed gas may be selectively fluidly connected to thepower unit. The reservoir may be configured for selective fluidconnection to the thermal well for enabling the flow of heat-transferliquid therebetween. A vent for venting expanded gas to atmosphere maybe selectively fluidly connected to the power unit.

In yet another aspect, embodiments of the invention feature a method ofenergy storage and recovery utilizing a power unit comprising a cylinderassembly for the compression of gas to store energy and/or the expansionof gas to recover energy. Gas is compressed and/or expanded in the powerunit. Prior to and/or during the compression and/or expansion, (i)heat-transfer liquid is withdrawn from a thermal well at a firsttemperature, (ii) the heat-transfer liquid is thermally conditioned,thereby bringing it to a second temperature different from the firsttemperature, and (iii the thermally conditioned heat-transfer liquid isintroduced into the gas to exchange heat therewith.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The heat exchange betweenthe gas and the thermally conditioned heat-transfer liquid may renderthe compression and/or expansion substantially isothermal. Introducingthe thermally conditioned heat-transfer liquid into the gas may includeor consist essentially of spraying the thermally conditionedheat-transfer liquid into the gas. Introducing the thermally conditionedheat-transfer liquid into the gas may form a foam including orconsisting essentially of the heat-transfer liquid and the gas. At leasta portion of the foam may be separated into gas and heat-transfer liquidafter the compression and/or expansion. Thermally conditioning theheat-transfer liquid may include or consist essentially of transfer ofthermal energy between the heat-transfer liquid and a second thermalwell discrete from and not fluidly connected to the thermal well. Wastethermal energy produced by the power unit may be stored in the secondthermal well. Thermal energy may be exchanged between the second thermalwell and the surrounding environment. Thermal energy may be exchangedbetween the second thermal well and the surrounding environment whilethe power unit is neither compressing nor expanding.

In an additional aspect, embodiments of the invention feature an energystorage and recovery system including or consisting essentially of (i) apower unit comprising a cylinder assembly for, therewithin, compressionof gas to store energy and/or expansion of gas to recover energy, (ii) amechanism for introducing heat-transfer liquid into the gas prior toand/or during the compression and/or expansion, (iii) selectivelyfluidly connected to the mechanism, a thermal well for containingheat-transfer liquid therein, (iv) a heat exchanger connected betweenthe thermal well and the power unit for thermally conditioningheat-transfer liquid flowing from the thermal well to the power unit,and (v) associated with the heat exchanger and discrete from the thermalwell, a second thermal well for storing thermal energy from and/orsupplying thermal energy to the heat-transfer fluid.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. A conduit may transferheat-transfer liquid introduced into the gas back into the thermal well.A waste-heat heat-exchange system for transferring waste thermal energyfrom the power unit to the second thermal well may be thermallyconnected to the power unit and the second thermal well. Anenvironmental heat-exchange system may be thermally connected to thesecond thermal well and the surrounding environment. The heat exchangermay be disposed within the second thermal well.

In yet an additional aspect, embodiments of the invention feature amethod of energy storage and recovery utilizing a power unit comprisinga cylinder assembly for the compression of gas to store energy and/orthe expansion of gas to recover energy. Gas is compressed or expanded inthe power unit. Prior to and/or during the compression and/or expansion,(i) heat-transfer liquid is withdrawn from a first thermal well at afirst temperature, and (ii) the heat-transfer liquid is introduced intothe gas to exchange heat therewith, the heat exchange bringing theheat-transfer liquid to a second temperature different from the firsttemperature. Heat-transfer liquid is transferred at the secondtemperature to a second thermal well discrete from and not fluidlyconnected to the first thermal well.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The heat exchange betweenthe gas and the heat-transfer liquid may render the compression and/orexpansion substantially isothermal. Introducing the heat-transfer liquidinto the gas may include or consist essentially of spraying thethermally conditioned heat-transfer liquid into the gas. Introducing theheat-transfer liquid into the gas may form a foam including orconsisting essentially of the heat-transfer liquid and the gas. At leasta portion of the foam may be separated into gas and heat-transfer liquidprior to transferring heat-transfer liquid to the second thermal well.Waste thermal energy produced by the power unit may be stored in thesecond thermal well. Thermal energy may be exchanged between thesurrounding environment and the first thermal well and/or the secondthermal well. Thermal energy may be exchanged with the surroundingenvironment while the power unit is neither compressing nor expanding.

In an aspect, embodiments of the invention feature an energy storage andrecovery system including (i) a power unit comprising a cylinderassembly for, therewithin, compression of gas to store energy and/orexpansion of gas to recover energy, (ii) a mechanism for introducingheat-transfer liquid into the gas prior to and/or during the compressionand/or expansion, (iii) selectively fluidly connected to the mechanism,(a) a first thermal well for containing heat-transfer liquid therein ata first temperature and (b) a second thermal well, discrete from thefirst thermal well, for containing heat-transfer liquid therein at asecond temperature different from the first temperature. The system alsoincludes a control system for (i) prior to and/or during compression,routing heat-transfer liquid (a) from the first thermal well into thegas and (b) from the power unit into the second thermal well, and (ii)prior to and/or during expansion, routing heat-transfer liquid (a) fromthe second thermal well into the gas and (b) from the power unit intothe first thermal well.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. A waste-heat heat-exchangesystem for transferring waste thermal energy from the power unit to thesecond thermal well may be thermally connected to the power unit and thesecond thermal well. An environmental heat-exchange system may bethermally connected to the first thermal well and the surroundingenvironment. An environmental heat-exchange system may be thermallyconnected to the second thermal well and the surrounding environment.

In another aspect, embodiments of the invention feature a method ofenergy storage and recovery utilizing a power unit comprising a cylinderassembly for the compression of gas to store energy and/or the expansionof gas to recover energy. Gas is compressed and/or expanded in the powerunit. Prior to and/or during the compression and/or expansion, (i)heat-transfer liquid is withdrawn from a reservoir at a firsttemperature, (ii) the heat-transfer liquid is thermally conditioned,thereby bringing it to a second temperature different from the firsttemperature, and (iii) the thermally conditioned heat-transfer liquid isintroduced into the gas to exchange heat therewith. Thermallyconditioning the heat-transfer liquid includes or consists essentiallyof exchanging thermal energy between the heat-transfer liquid and aheat-storage liquid flowing from a first thermal well having a thirdtemperature to a second thermal well (i) discrete from the first thermalwell and (ii) having a fourth temperature different from the thirdtemperature.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The heat-transfer liquid andthe heat-storage liquid may not mix during thermal conditioning of theheat-transfer liquid. The heat exchange between the gas and thethermally conditioned heat-transfer liquid may render the compressionand/or expansion substantially isothermal. Introducing the thermallyconditioned heat-transfer liquid into the gas may include or consistessentially of spraying the thermally conditioned heat-transfer liquidinto the gas. Introducing the thermally conditioned heat-transfer liquidinto the gas may form a foam including or consisting essentially of theheat-transfer fluid and the gas. At least a portion of the foam may beseparated into gas and heat-transfer liquid after the compression and/orexpansion.

In yet another aspect, embodiments of the invention feature an energystorage and recovery system including or consisting essentially of (i) apower unit comprising a cylinder assembly for, therewithin, compressionof gas to store energy and/or expansion of gas to recover energy, (ii) amechanism for introducing heat-transfer liquid into the gas prior toand/or during the compression and/or expansion, (iii) selectivelyfluidly connected to the mechanism, a reservoir for containingheat-transfer liquid therein, (iv) a heat exchanger connected betweenthe reservoir and the power unit for thermally conditioningheat-transfer liquid flowing from the reservoir to the power unit, and(v) associated with the heat exchanger and not fluidly connected to thereservoir, (a) a first thermal well for containing heat-storage liquidat a first temperature and (b) a second thermal well for containingheat-storage liquid at a second temperature different from the firsttemperature, the flow of heat-storage liquid between the first andsecond thermal wells thermally conditioning the heat-transfer fluid.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. A conduit may transferheat-transfer liquid introduced into the gas back into the reservoir. Awaste-heat heat-exchange system for transferring waste thermal energyfrom the power unit to the second thermal well may be thermallyconnected to the power unit and the second thermal well. Anenvironmental heat-exchange system may be thermally connected to thefirst thermal well and the surrounding environment. An environmentalheat-exchange system may be thermally connected to the second thermalwell and the surrounding environment.

In an additional aspect, embodiments of the invention feature a methodof energy storage and recovery utilizing a power unit comprising acylinder assembly for the compression of gas to store energy and/or theexpansion of gas to recover energy. Gas is compressed in the power unit.Prior to and/or during the compression, (i) heat-transfer liquid iswithdrawn from a liquid reservoir at a first temperature, and (ii) theheat-transfer liquid is introduced into the gas to exchange heattherewith, the heat exchange bringing the heat-transfer liquid to asecond temperature higher than the first temperature. Both theheat-transfer liquid at the second temperature and the compressed gasare transferred to a compressed-gas store.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. The heat exchange betweenthe gas and the heat-transfer liquid may render the compressionsubstantially isothermal. Introducing the heat-transfer liquid into thegas may include or consist essentially of spraying the thermallyconditioned heat-transfer liquid into the gas. Introducing theheat-transfer liquid into the gas may form a foam including orconsisting essentially of the heat-transfer liquid and the gas.Transferring both the heat-transfer liquid at the second temperature andthe compressed gas to a compressed-gas store may include or consistessentially of transferring the foam to the compressed-gas store.

The method may include (i) transferring compressed gas from thecompressed-gas store to the power unit, (ii) expanding the compressedgas in the power unit, (iii) prior to and/or during the expansion, (a)withdrawing heat-transfer liquid from the compressed-gas store at athird temperature and (b) introducing the heat-transfer liquid into thegas to exchange heat therewith, the heat exchange bringing theheat-transfer liquid to a fourth temperature lower than the thirdtemperature, and (iv) transferring the heat-transfer liquid to theliquid reservoir. The heat exchange between the gas and theheat-transfer liquid may render the expansion substantially isothermal.Introducing the heat-transfer liquid into the gas prior to and/or duringexpansion may include or consist essentially of spraying the thermallyconditioned heat-transfer liquid into the gas. Introducing theheat-transfer liquid into the gas prior to and/or during expansion mayform a foam including or consisting essentially of the heat-transferliquid and the gas. At least a portion of the foam may be separated intogas and heat-transfer liquid prior to transferring the heat-transferliquid to the liquid reservoir. Waste thermal energy produced by thepower unit may be stored in the compressed-gas store. Thermal energy maybe exchanged between the surrounding environment and the compressed-gasstore. Thermal energy may be exchanged with the surrounding environmentwhile the power unit is neither compressing nor expanding.

In yet an additional aspect, embodiments of the invention feature amethod of energy storage and recovery utilizing a power unit comprisinga cylinder assembly for the compression of gas to store energy and/orthe expansion of gas to recover energy. Gas is compressed in the powerunit. Prior to and/or during the compression, (i) heat-transfer liquidis withdrawn from a first thermal well at a first temperature, and (ii)the heat-transfer liquid is introduced into the gas to exchange heattherewith, the heat exchange bringing the heat-transfer liquid to asecond temperature higher than the first temperature. The compressed gasis transferred to a compressed-gas store. The heat-transfer liquid atthe second temperature is transferred to the compressed-gas store and/ora second thermal well discrete from the first thermal well.

The method may include (i) transferring compressed gas from thecompressed-gas store to the power unit, (ii) expanding the compressedgas in the power unit, (iii) prior to and/or during the expansion, (a)withdrawing heat-transfer liquid from at least one of the compressed-gasstore or the second thermal well, and (b) introducing the heat-transferliquid into the gas to exchange heat therewith, and (iv) transferringthe heat-transfer liquid to the first thermal well.

Embodiments of the invention incorporate one or more of the following inany of a variety of different combinations. Expanding the compressed gasin the power unit may include or consist essentially of expanding thecompressed gas in a first stage and a second stage each spanning adifferent pressure range. Heat-transfer liquid may be withdrawn from thecompressed-gas store prior to and/or during expansion in the firststage. Heat-transfer liquid may be withdrawn from the second thermalwell prior to and/or during expansion in the second stage. The heatexchange between the gas and the heat-transfer liquid prior to and/orduring the expansion may render the expansion substantially isothermal.Introducing the heat-transfer liquid into the gas prior to and/or duringexpansion may include or consist essentially of spraying the thermallyconditioned heat-transfer liquid into the gas. Introducing theheat-transfer liquid into the gas may form a foam including orconsisting essentially of the heat-transfer liquid and the gas. At leasta portion of the foam may be separated into gas and heat-transfer liquidprior to transferring the heat-transfer liquid to the first thermalwell. Compressing the gas in the power unit may include or consistessentially of compressing the gas in a first stage and a second stageeach spanning a different pressure range. Heat-transfer liquid may betransferred to the compressed-gas store after or during compression inthe first stage. Heat-transfer liquid may be transferred to the secondthermal well after or during compression in the second stage. The heatexchange between the gas and the heat-transfer liquid prior to and/orduring compression may render the compression substantially isothermal.Introducing the heat-transfer liquid into the gas prior to and/or duringcompression may include or consist essentially of spraying the thermallyconditioned heat-transfer liquid into the gas. Introducing theheat-transfer liquid into the gas prior to and/or during compression mayform a foam including or consisting essentially of the heat-transferliquid and the gas. At least a portion of the foam may be separated intogas and heat-transfer liquid before transferring the heat-transferliquid at the second temperature to the compressed-gas store and/or asecond thermal well discrete from the first thermal well. Waste thermalenergy produced by the power unit may be stored in the second thermalwell. Thermal energy may be exchanged between the surroundingenvironment and the first thermal well and/or the second thermal well.Thermal energy may be exchanged with the surrounding environment whilethe power unit is neither compressing nor expanding.

These and other objects, along with advantages and features of theinvention, will become more apparent through reference to the followingdescription, the accompanying drawings, and the claims. Furthermore, itis to be understood that the features of the various embodimentsdescribed herein are not mutually exclusive and can exist in variouscombinations and permutations. Note that as used herein, the terms“pipe,” “piping” and the like shall refer to one or more conduits thatare rated to carry gas or liquid between two points. Thus, the singularterm should be taken to include a plurality of parallel conduits whereappropriate. Herein, the terms “liquid” and “water” interchangeablyconnote any mostly or substantially incompressible liquid, the terms“gas” and “air” are used interchangeably, and the term “fluid” may referto a liquid, a gas, or a mixture of liquid and gas (e.g., a foam) unlessotherwise indicated. As used herein unless otherwise indicated, theterms “approximately” and “substantially” mean±10%, and, in someembodiments, ±5%. A “valve” is any mechanism or component forcontrolling fluid communication between fluid paths or reservoirs, orfor selectively permitting control or venting. The term “cylinder”refers to a chamber, of uniform but not necessarily circularcross-section, which may contain a slidably disposed piston or othermechanism that separates the fluid on one side of the chamber from thaton the other, preventing fluid movement from one side of the chamber tothe other while allowing the transfer of force/pressure from one side ofthe chamber to the next or to a mechanism outside the chamber. At leastone of the two ends of a chamber may be closed by end caps, also hereintermed “heads.” As utilized herein, an “end cap” is not necessarily acomponent distinct or separable from the remaining portion of thecylinder, but may refer to an end portion of the cylinder itself. Rods,valves, and other devices may pass through the end caps. A “cylinderassembly” may be a simple cylinder or include multiple cylinders, andmay or may not have additional associated components (such as mechanicallinkages among the cylinders). The shaft of a cylinder may be coupledhydraulically or mechanically to a mechanical load (e.g., a hydraulicmotor/pump or a crankshaft) that is in turn coupled to an electricalload (e.g., rotary or linear electric motor/generator attached to powerelectronics and/or directly to the grid or other loads), as described inthe '678 and '842 patents. As used herein, “thermal conditioning” of aheat-exchange fluid does not include any modification of the temperatureof the heat-exchange fluid resulting from interaction with gas withwhich the heat-exchange fluid is exchanging thermal energy; rather, suchthermal conditioning generally refers to the modification of thetemperature of the heat-exchange fluid by other means (e.g., an externalheat exchanger). The terms “heat-exchange” and “heat-transfer” aregenerally utilized interchangeably herein. Unless otherwise indicated,motor/pumps described herein are not required to be configured tofunction both as a motor and a pump if they are utilized during systemoperation only as a motor or a pump but not both. Gas expansionsdescribed herein may be performed in the absence of combustion (asopposed to the operation of an internal-combustion cylinder, forexample).

BRIEF DESCRIPTION OF THE DRAWINGS

In the drawings, like reference characters generally refer to the sameparts throughout the different views. Cylinders, rods, and othercomponents are depicted in cross section in a manner that will beintelligible to all persons familiar with the art of pneumatic andhydraulic cylinders. Also, the drawings are not necessarily to scale,emphasis instead generally being placed upon illustrating the principlesof the invention. In the following description, various embodiments ofthe present invention are described with reference to the followingdrawings, in which:

FIG. 1 is a schematic drawing of a compressed-gas energy storage systemin accordance with various embodiments of the invention;

FIG. 2 is a schematic drawing of various components of a compressed-gasenergy storage system in accordance with various embodiments of theinvention;

FIG. 3 is a schematic drawing of the major components of a compressedair energy storage and recovery system in accordance with variousembodiments of the invention;

FIG. 4 is a schematic drawing of various components of a multi-cylindercompressed-gas energy storage system in accordance with variousembodiments of the invention;

FIG. 5 is a schematic drawing of a cylinder assembly with apparatus forthe generation of foam external to the cylinder in accordance withvarious embodiments of the invention;

FIG. 6 is a schematic drawing of a cylinder assembly with apparatus forthe generation of foam external to the cylinder and provision forbypassing the foam-generating apparatus in accordance with variousembodiments of the invention;

FIG. 7 is a schematic drawing of a cylinder assembly with apparatus forthe generation of foam in a vessel external to the cylinder inaccordance with various embodiments of the invention;

FIG. 8 is a schematic drawing of a cylinder assembly with apparatus forthe generation of foam internal to the cylinder in accordance withvarious embodiments of the invention;

FIG. 9 is a schematic drawing of a cylinder assembly having twocylinders and apparatus for the generation and separation of foamexternal to the cylinders in accordance with various embodiments of theinvention;

FIG. 10 is a graph of experimental data on the energetic performance ofdroplet sprays in isothermal gas expansions in accordance with variousembodiments of the invention;

FIG. 11 is a graph of experimental data on the energetic performance offoam in isothermal gas expansions in accordance with various embodimentsof the invention;

FIG. 12 is a graph of experimental data on the energetic performance ofdroplet sprays in isothermal gas compressions in accordance with variousembodiments of the invention;

FIG. 13 is a graph of experimental data on the energetic performance offoam in isothermal gas compressions in accordance with variousembodiments of the invention;

FIG. 14 is a graph of spray pressures calculated for two methods ofintroducing a foaming liquid into a cylinder during a compression cyclein accordance with various embodiments of the invention;

FIG. 15 is a graph of final liquid temperatures calculated forcompressions over a range of heat-exchange foam mass ratios and finalcompression pressures in accordance with various embodiments of theinvention;

FIG. 16 is a graph of the additional storage space calculated asrequired for a range of heat-exchange foam mass ratios in accordancewith various embodiments of the invention;

FIG. 17 is a plot of experimental data on the isothermal efficiencies ofa gas-expansion compressions using a foam in accordance with variousembodiments of the invention, compared to the isothermal efficiencies ofsimilar compressions with non-foaming spray;

FIG. 18 is a schematic drawing of a cylinder assembly having twocylinders and apparatus for the generation and separation of foamshaving three different mass ratios in accordance with variousembodiments of the invention;

FIG. 19 is a schematic drawing of an apparatus for the generation offoam having a relatively low mass ratio in accordance with variousembodiments of the invention;

FIG. 20 is a schematic drawing of an apparatus for the generation andseparation of foam having a relatively high mass ratio in accordancewith various embodiments of the invention;

FIG. 21 is a schematic drawing of an apparatus for the generation offoam having a relatively low mass ratio in accordance with variousembodiments of the invention;

FIG. 22 is a schematic drawing of an apparatus for the generation offoam having an intermediate mass ratio in accordance with variousembodiments of the invention;

FIG. 23 is a schematic drawing of various components of a compressed-gasenergy storage system in accordance with various embodiments of theinvention;

FIGS. 24A and 24B are schematic drawings of various components of apneumatic cylinder additionally functional as a liquid pump inaccordance with various embodiments of the invention;

FIG. 25 is a schematic drawing of various components of a compressed-gasenergy storage system employing two pneumatic cylinders additionallyfunctional as liquid pumps in accordance with various embodiments of theinvention;

FIG. 26 is a schematic drawing of two poppet valves in a cylinder headin accordance with various embodiments of the invention;

FIG. 27 is a schematic drawing of various components of a compressed-gasenergy storage system in accordance with various embodiments of theinvention;

FIG. 28 is a schematic drawing of various components of a compressed-gasenergy storage system, accompanied by a graph showing selected time andtemperature relationships within the system, in accordance with variousembodiments of the invention;

FIG. 29 is a schematic drawing of various components of a compressed-gasenergy storage system in accordance with various embodiments of theinvention;

FIG. 30 is a schematic drawing of compressed-gas storage vessels with anexternal heat exchanger in accordance with various embodiments of theinvention;

FIG. 31 is a schematic drawing of compressed-gas storage vessels withinternal heat exchange in accordance with various embodiments of theinvention;

FIG. 32 is a schematic drawing of compressed-gas storage vessels warmedor cooled by a fluid circulating around them in accordance with variousembodiments of the invention;

FIG. 33 is a schematic drawing of compressed-gas storage vessels warmedor cooled by a liquid circulating around them in accordance with variousembodiments of the invention;

FIG. 34 is a schematic drawing of a cavern storing compressed gas andheat-exchange liquid, with external heat exchange in accordance withvarious embodiments of the invention;

FIG. 35 is a schematic of various components of an energy storage andrecovery system in accordance with various embodiments of the invention,illustrating an application where waste heat from a power plant is usedto heat stored compressed gas prior to and/or during expansion in thesystem;

FIGS. 36 and 37 are schematic drawings of energy storage and recoverysystems incorporating a cylinder assembly and one or more expanders,compressors, or expander/compressors in accordance with variousembodiments of the invention;

FIG. 38 is a schematic drawing of a booster pump equipped for theformation of foam therewithin in accordance with various embodiments ofthe invention;

FIGS. 39-44 are schematic drawings of various systems featuring cylinderassemblies for expansion and/or compression of gas, as well as one ormore thermal wells, in accordance with various embodiments of theinvention;

FIGS. 45 and 46 are schematics of various components of energy storageand recovery systems in which high-power, short-duration energy storagedevices are connected in parallel with a compressed-gas energy storagesystem, in accordance with various embodiments of the invention;

FIG. 47 is an illustrative plot of electricity supply and demand for anexemplary 24-hour period;

FIG. 48 is an illustrative plot of the response of a combinedhigh-power, short-duration energy storage device and compressed-gasenergy storage system, in accordance with various embodiments of theinvention, on electricity supply and demand for the 24-hour period ofFIG. 47;

FIG. 49 is an illustrative plot of the state-of-charge of a combinedhigh-power, short-duration energy storage device and compressed gasenergy storage system, in accordance with various embodiments of theinvention, for the 24-hour period of FIG. 47; and

FIG. 50 is a conceptual drawing of an illustrative power generation andconsumption network or grid in accordance with various embodiments ofthe invention.

DETAILED DESCRIPTION

FIG. 1 depicts an illustrative system 100 that may be part of a largersystem, not otherwise depicted, for the storage and release of energy.Subsequent figures will clarify the application of embodiments of theinvention to such a system. The system 100 depicted in FIG. 1 featuresan assembly 101 for compressing and expanding gas. Expansion/compressionassembly 101 may include or consist essentially of either one or moreindividual devices for expanding or compressing gas (e.g., turbines orcylinder assemblies that each may house a moveable boundary mechanism)or a staged series of such devices, as well as ancillary devices (e.g.,valves) not depicted explicitly in FIG. 1.

An electric motor/generator 102 (e.g., a rotary or linear electricmachine) is in physical communication (e.g., via hydraulic pump, pistonshaft, or mechanical crankshaft) with the expansion/compression assembly101. The motor/generator 102 may be electrically connected to a sourceand/or sink of electric energy not explicitly depicted in FIG. 1 (e.g.,an electrical distribution grid or a source of renewable energy such asone or more wind turbines or solar cells).

The expansion/compression assembly 101 may be in fluid communicationwith a heat-transfer subsystem 104 that alters the temperature and/orpressure of a fluid (i.e., gas, liquid, or gas-liquid mixture such as afoam) extracted from expansion/compression assembly 101 and, afteralteration of the fluid's temperature and/or pressure, returns at leasta portion of it to expansion/compression assembly 101. Heat-transfersubsystem 104 may include pumps, valves, and other devices (not depictedexplicitly in FIG. 1) ancillary to its heat-transfer function and to thetransfer of fluid to and from expansion/compression assembly 101.Operated appropriately, the heat-transfer subsystem 104 enablessubstantially isothermal compression and/or expansion of gas insideexpansion/compression assembly 101.

Connected to the expansion/compression assembly 101 is a pipe 106 with acontrol valve 108 that controls a flow of fluid (e.g., gas) betweenassembly 101 and a storage reservoir 112 (e.g., one or more pressurevessels, pipes, and/or caverns). The storage reservoir 112 may be influid communication with a heat-transfer subsystem 114 that alters thetemperature and/or pressure of fluid removed from storage reservoir 112and, after alteration of the fluid's temperature and/or pressure,returns it to storage reservoir 112. A second pipe 116 with a controlvalve 118 may be in fluid communication with the expansion/compressionassembly 101 and with a vent 120 that communicates with a body of gas atrelatively low pressure (e.g., the ambient atmosphere).

A control system 122 receives information inputs from any ofexpansion/compression assembly 101, storage reservoir 112, and othercomponents of system 100 and sources external to system 100. Theseinformation inputs may include or consist essentially of pressure,temperature, and/or other telemetered measurements of properties ofcomponents of system 101. Such information inputs, here genericallydenoted by the letter “T,” are transmitted to control system 122 eitherwirelessly or through wires. Such transmission is denoted in FIG. 1 bydotted lines 124, 126.

The control system 122 may selectively control valves 108 and 118 toenable substantially isothermal compression and/or expansion of a gas inassembly 101. Control signals, here generically denoted by the letter“C,” are transmitted to valves 108 and 118 either wirelessly or throughwires. Such transmission is denoted in FIG. 1 by dashed lines 128, 130.The control system 122 may also control the operation of theheat-transfer assemblies 104, 114 and of other components not explicitlydepicted in FIG. 1. The transmission of control and telemetry signalsfor these purposes is not explicitly depicted in FIG. 1.

The control system 122 may be any acceptable control device with ahuman-machine interface. For example, the control system 122 may includea computer (for example a PC-type) that executes a stored controlapplication in the form of a computer-readable software medium. Moregenerally, control system 122 may be realized as software, hardware, orsome combination thereof. For example, control system 122 may beimplemented on one or more computers, such as a PC having a CPU boardcontaining one or more processors such as the Pentium, Core, Atom, orCeleron family of processors manufactured by Intel Corporation of SantaClara, Calif., the 680×0 and POWER PC family of processors manufacturedby Motorola Corporation of Schaumburg, Ill., and/or the ATHLON line ofprocessors manufactured by Advanced Micro Devices, Inc., of Sunnyvale,Calif. The processor may also include a main memory unit for storingprograms and/or data relating to the methods described above. The memorymay include random access memory (RAM), read only memory (ROM), and/orFLASH memory residing on commonly available hardware such as one or moreapplication specific integrated circuits (ASIC), field programmable gatearrays (FPGA), electrically erasable programmable read-only memories(EEPROM), programmable read-only memories (PROM), programmable logicdevices (PLD), or read-only memory devices (ROM). In some embodiments,the programs may be provided using external RAM and/or ROM such asoptical disks, magnetic disks, or other storage devices.

For embodiments in which the functions of controller 122 are provided bysoftware, the program may be written in any one of a number ofhigh-level languages such as FORTRAN, PASCAL, JAVA, C, C++, C#, LISP,PERL, BASIC or any suitable programming language. Additionally, thesoftware can be implemented in an assembly language and/or machinelanguage directed to the microprocessor resident on a target device.

As described above, the control system 122 may receive telemetry fromsensors monitoring various aspects of the operation of system 100, andmay provide signals to control valve actuators, valves, motors, andother electromechanical/electronic devices. Control system 122 maycommunicate with such sensors and/or other components of system 100 (andother embodiments described herein) via wired or wireless communication.An appropriate interface may be used to convert data from sensors into aform readable by the control system 122 (such as RS-232 or network-basedinterconnects). Likewise, the interface converts the computer's controlsignals into a form usable by valves and other actuators to perform anoperation. The provision of such interfaces, as well as suitable controlprogramming, is clear to those of ordinary skill in the art and may beprovided without undue experimentation.

System 100 may be operated so as to compress gas admitted through thevent 120 and store the gas thus compressed in reservoir 112. Forexample, in an initial state of operation, valve 108 is closed and valve118 is open, admitting a quantity of gas into expansion/compressionassembly 101. When a desired quantity of gas has been admitted intoassembly 101, valve 118 may be closed. The motor/generator 102,employing energy supplied by a source not explicitly depicted in FIG. 1(e.g., the electrical grid), then provides mechanical power toexpansion/compression assembly 101, enabling the gas within assembly 101to be compressed.

During compression of the gas within assembly 101, fluid (i.e., gas,liquid, or a gas-liquid mixture) may be circulated between assembly 101and heat-exchange assembly 104. Heat-exchange assembly 104 may beoperated in such a manner as to enable substantially isothermalcompression of the gas within assembly 101. During or after compressionof the gas within assembly 101, valve 108 may be opened to enablehigh-pressure fluid (e.g., compressed gas or a mixture of liquid andcompressed gas) to flow to reservoir 112. Heat-exchange assembly 114 maybe operated at any time in such a manner as alter the temperature and/orpressure of the fluid within reservoir 112.

That system 100 may also be operated so as to expand compressed gas fromreservoir 112 in expansion/compression assembly 101 in such a manner asto deliver energy to the motor/generator 102 will be apparent to allpersons familiar with the operation of pneumatic, hydraulic, andelectric machines.

FIG. 2 depicts an illustrative system 200 that features a cylinderassembly 201 (i.e., an embodiment of assembly 101 in FIG. 1) incommunication with a reservoir 222 (112 in FIG. 1) and a vent toatmosphere 223 (120 in FIG. 1). In the illustrative system 200 shown inFIG. 2, the cylinder assembly 201 contains a piston 202 slidablydisposed therein. In some embodiments the piston 202 is replaced by adifferent boundary mechanism dividing cylinder assembly 201 intomultiple chambers, or piston 202 is absent entirely, and cylinderassembly 201 is a “liquid piston.” The cylinder assembly 201 may bedivided into, e.g., two pneumatic chambers or one pneumatic chamber andone hydraulic chamber. The piston 202 is connected to a rod 204, whichmay contain a center-drilled fluid passageway with fluid outlet 212extending from the piston 202. The rod 204 is also attached to, e.g., amechanical load (e.g., a crankshaft or a hydraulic system) that is notdepicted. The cylinder assembly 201 is in liquid communication with aheat-transfer subsystem 224 that includes or consists essentially of acirculation pump 214 and a spray mechanism 210 to enable substantiallyisothermal compression/expansion of gas. Heat-transfer fluid circulatedby pump 214 may be passed through a heat exchanger 203 (e.g.,tube-in-shell- or parallel-plate-type heat exchanger). Spray mechanism210 may include or consist essentially of one or more spray heads (e.g.,disposed at one end of cylinder assembly 201) and/or spray rods (e.g.,extending along at least a portion of the central axis of cylinderassembly 201). In other embodiments, the spray mechanism 210 is omittedand a foam, rather than a spray of droplets, is created to facilitateheat exchange between liquid and gas during compression and expansion ofgas within the cylinder assembly 201. Foam may be generated by foaminggas with heat-exchange liquid in a mechanism (not shown, described inmore detail below) external to the cylinder assembly 201 and theninjecting the resulting foam into the cylinder assembly 201.Alternatively or additionally, foam may be generated inside the cylinderassembly 201 by the injection of heat-exchange liquid into cylinderassembly 201 through a foam-generating mechanism (e.g., spray head,rotating blade, one or more nozzles), partly or entirely filling thepneumatic chamber of cylinder assembly 201. In some embodiments,droplets and foams may be introduced into cylinder assembly 201simultaneously and/or sequentially. Various embodiments may featuremechanisms (not shown in FIG. 2) for controlling the characteristics offoam (e.g., bubble size) and for breaking down, separating, and/orregenerating foam.

System 200 further includes a first control valve 220 (108 in FIG. 1) incommunication with a storage reservoir 222 and cylinder assembly 201,and a second control valve 221 (118 in FIG. 1) in communication with avent 223 and cylinder assembly 201. A control system 226 (122 in FIG. 1)may control operation of, e.g., valves 222 and 221 based on varioussystem inputs (e.g., pressure, temperature, piston position, and/orfluid state) from cylinder assembly 201 and/or storage reservoir 222.Heat-transfer fluid (liquid or circulated by pump 214 enters throughpipe 213. Pipe 213 may be (a) connected to a low-pressure fluid source(e.g., fluid reservoir (not shown) at the pressure to which vent 223 isconnected or thermal well 242); (b) connected to a high-pressure source(e.g., fluid reservoir (not shown) at the pressure of reservoir 222);(c) selectively connected (using valve arrangement not shown) to lowpressure during a compression process and to high pressure during anexpansion process; (d) connected to changing-pressure fluid 208 in thecylinder 201 via connection 212; or (e) some combination of theseoptions.

In an initial state, the cylinder assembly 201 may contain a gas 206(e.g., air introduced to the cylinder assembly 201 via valve 221 andvent 223) and a heat-transfer fluid 208 (which may include or consistessentially of, e.g., water or another suitable liquid). When the gas206 enters the cylinder assembly 201, piston 202 is operated to compressthe gas 206 to an elevated pressure (e.g., approximately 3,000 psi).Heat-transfer fluid (not necessarily the identical body of heat-transferfluid 208) flows from pipe 213 to the pump 214. The pump 214 may raisethe pressure of the heat-exchange fluid to a pressure (e.g., up toapproximately 3,015 psig) somewhat higher than the pressure within thecylinder assembly 201, as described in the '409 application.Alternatively or in conjunction, embodiments of the invention add heat(i.e., thermal energy) to, or remove heat from, the high-pressure gas inthe cylinder assembly 201 by passing only relatively low-pressure fluidsthrough a heat exchanger or fluid reservoir, as detailed in U.S. patentapplication Ser. No. 13/211,440, filed Aug. 17, 2011 (the '440application), the entire disclosure of which is incorporated byreference herein.

Heat-transfer fluid is then sent through a pipe 216, where it may bepassed through a heat exchanger 203 (where its temperature is altered)and then through a pipe 218 to the spray mechanism 210. Theheat-transfer fluid thus circulated may include or consist essentiallyof liquid or foam. Spray mechanism 210 may be disposed within thecylinder assembly 201, as shown; located in the storage vessel 222 orvent 223; or located in piping or manifolding around the cylinderassembly, such as pipe 218 or the pipes connecting the cylinder assemblyto storage vessel 222 or vent 223. The spray mechanism 210 may beoperated in the vent 223 or connecting pipes during compression, and aseparate spray mechanism may be operated in the storage vessel 222 orconnecting pipes during expansion. Heat-transfer spray 211 from spraymechanism 210 (and/or any additional spray mechanisms), and/or foam frommechanisms internal or external to the cylinder assembly 101, enablesubstantially isothermal compression of gas 206 within cylinder assembly201.

In some embodiments, the heat exchanger 203 is configured to conditionheat-transfer fluid at low pressure (e.g., a pressure lower than themaximum pressure of a compression or expansion stroke in cylinderassembly 201), and heat-transfer fluid is thermally conditioned betweenstrokes or only during portions of strokes, as detailed in the '440application. Embodiments of the invention are configured for circulationof heat-transfer fluid without the use of hoses that flex duringoperation through the use of, e.g., tubes or straws configured fornon-flexure and/or pumps (e.g., submersible bore pumps, axial flowpumps, or other in-line style pumps) internal to the cylinder assembly(e.g., at least partially disposed within the piston rod thereof), asdescribed in U.S. patent application Ser. No. 13/234,239, filed Sep. 16,2011 (the '239 application), the entire disclosure of which isincorporated by reference herein.

At or near the end of the compression stroke, control system 226 opensvalve 220 to admit the compressed gas 206 to the storage reservoir 222.Operation of valves 220 and 221 may be controlled by various inputs tocontrol system 226, such as piston position in cylinder assembly 201,pressure in storage vessel 222, pressure in cylinder assembly 201,and/or temperature in cylinder assembly 201.

As mentioned above, the control system 226 may enforce substantiallyisothermal operation, i.e., expansion and/or compression of gas incylinder assembly 201, via control over, e.g., the introduction of gasinto and the exhausting of gas out of cylinder assembly 201, the ratesof compression and/or expansion, and/or the operation of theheat-exchange subsystem in response to sensed conditions. For example,control system 226 may be responsive to one or more sensors disposed inor on cylinder assembly 201 for measuring the temperature of the gasand/or the heat-exchange fluid within cylinder assembly 201, respondingto deviations in temperature by issuing control signals that operate oneor more of the system components noted above to compensate, in realtime, for the sensed temperature deviations. For example, in response toa temperature increase within cylinder assembly 201, control system 226may issue commands to increase the flow rate of spray 211 ofheat-exchange fluid 208.

Furthermore, embodiments of the invention may be applied to systems inwhich cylinder assembly 201 (or a chamber thereof) is in fluidcommunication with a pneumatic chamber of a second cylinder (e.g., asshown in FIG. 4). That second cylinder, in turn, may communicatesimilarly with a third cylinder, and so forth. Any number of cylindersmay be linked in this way. These cylinders may be connected in parallelor in a series configuration, where the compression and expansion isdone in multiple stages.

The fluid circuit of heat exchanger 203 may be filled with water, acoolant mixture, an aqueous foam, or any other acceptable heat-exchangemedium. In alternative embodiments, a gas, such as air or refrigerant,is used as the heat-exchange medium. In general, the fluid is routed byconduits to a large reservoir of such fluid in a closed or open loop.One example of an open loop is a well or body of water from whichambient water is drawn and the exhaust water is delivered to a differentlocation, for example, downstream in a river. In a closed-loopembodiment, a cooling tower may cycle the water through the air forreturn to the heat exchanger. Likewise, water may pass through asubmerged or buried coil of continuous piping where a counterheat-exchange occurs to return the fluid flow to ambient temperaturebefore it returns to the heat exchanger for another cycle.

In various embodiments, the heat-exchange fluid is conditioned (i.e.,pre-heated and/or pre-chilled) or used for heating or cooling needs byconnecting the fluid inlet 238 and fluid outlet 240 of the externalheat-exchange side of the heat exchanger 203 to an installation such asa heat-engine power plant, an industrial process with waste heat, a heatpump, and/or a building needing space heating or cooling, as describedin the '731 patent. Alternatively, the external heat-exchange side ofthe heat exchanger 203 may be connected to a thermal well 242 asdepicted in FIG. 2. The thermal well 242 may include or consistessentially of a large water reservoir that acts as aconstant-temperature thermal fluid source for use with the system.Alternatively, the water reservoir may be thermally linked to waste heatfrom an industrial process or the like, as described above, via anotherheat exchanger contained within the installation. This allows theheat-exchange fluid to acquire or expel heat from/to the linked process,depending on configuration, for later use as a heating/cooling medium inthe energy storage/conversion system. Alternatively, the thermal well242 may include two or more bodies of energy-storage medium, e.g., ahot-water thermal well and a cold-water thermal well, that are typicallymaintained in contrasting energy states in order to increase the energyof system 200 compared with a system in which thermal well 242 includesa single body of energy-storage medium. Storage media other than watermay be utilized in the thermal well 242; temperature changes, phasechanges, or both may be employed by storage media of thermal well 242 tostore and release energy. Thermal or fluid links (not shown) to theatmosphere, ground, and/or other components of the environment may alsobe included in system 200, allowing mass, thermal energy, or both to beadded to or removed from the thermal well 242. Moreover, as depicted inFIG. 2, the heat-transfer subsystem 224 does not interchange fluiddirectly with the thermal well 242, but in other embodiments, fluid ispassed directly between the heat-transfer subsystem 224 and the thermalwell 242 with no heat exchanger maintaining separation between fluids.

FIG. 3 is a schematic of the major components of an illustrative system300 that employs a pneumatic cylinder 302 to efficiently convert (i.e.,store) mechanical energy into the potential energy of compressed gasand, in another mode of operation, efficiently convert (i.e., recover)the potential energy of compressed gas into mechanical work. Thepneumatic cylinder 302 may contain a slidably disposed piston 304 thatdivides the interior of the cylinder 302 into a distal chamber 306 and aproximal chamber 308. A port or ports (not shown) with associated pipes312 and a bidirectional valve 316 enables gas from a high-pressurestorage reservoir 320 to be admitted to chamber 306 as desired. A portor ports (not shown) with associated pipes 322 and a bidirectional valve324 enables gas from the chamber 306 to be exhausted through a vent 326to the ambient atmosphere as desired. In alternate embodiments, vent 326is replaced by additional lower-pressure pneumatic cylinders (orpneumatic chambers of cylinders). A port or ports (not shown) enablesthe interior of the chamber 308 to communicate freely at all times withthe ambient atmosphere. In alternate embodiments, cylinder 302 isdouble-acting and chamber 308 is, like chamber 306, equipped to admitand exhaust fluids in various states of operation. The distal end of arod 330 is coupled to the piston 304. The rod 330 may be connected to acrankshaft, hydraulic cylinder, or other mechanisms for convertinglinear mechanical motion to useful work as described in the '678 and'842 patents.

In the energy recovery or expansion mode of operation, storage reservoir320 is filled with high-pressure air (or other gas) 332 and a quantityof heat-transfer fluid 334. The heat-transfer fluid 334 may be anaqueous foam or a liquid that tends to foam when sprayed or otherwiseacted upon. The liquid component of the aqueous foam, or the liquid thattends to foam, may include or consist essentially of water with 2% to 5%of certain additives; these additives may also provide functions ofanti-corrosion, anti-wear (lubricity), anti-biogrowth (biocide),freezing-point modification (anti-freeze), and/or surface-tensionmodification. Additives may include a micro-emulsion of a lubricatingfluid such as mineral oil, a solution of agents such as glycols (e.g.propylene glycol), or soluble synthetics (e.g. ethanolamines). Suchadditives tend to reduce liquid surface tension and lead to substantialfoaming when sprayed. Commercially available fluids may be used at anapproximately 5% solution in water, such as Mecagreen 127 (availablefrom the Condat Corporation of Michigan), which consists in part of amicro-emulsion of mineral oil, and Quintolubric 807-WP (available fromthe Quaker Chemical Corporation of Pennsylvania), which consists in partof a soluble ethanolamine. Other additives may be used at higherconcentrations (such as at a 50% solution in water), including Cryo-tek100/Al (available from the Hercules Chemical Company of New Jersey),which consists in part of a propylene glycol. These fluids may befurther modified to enhance foaming while being sprayed and to speeddefoaming when in a reservoir.

The heat-transfer fluid 334 may be circulated within the storagereservoir 320 via high-inlet-pressure, low-power-consumption pump 336(such as described in the '731 patent). In various embodiments, thefluid 334 may be removed from the bottom of the storage reservoir 320via piping 338, circulated via pump 336 through a heat exchanger 340,and introduced (e.g., sprayed) back into the top of storage reservoir320 via piping 342 and spray head 344 (or other suitable mechanism). Anychanges in pressure within reservoir 320 due to removal or addition ofgas (e.g., via pipe 312) generally tend to result in changes intemperature of the gas 332 within reservoir 320. By spraying and/orfoaming the fluid 334 throughout the storage reservoir gas 332, heat maybe added to or removed from the gas 332 via heat exchange with theheat-transfer fluid 334. By circulating the heat-transfer fluid 334through heat exchanger 340, the temperature of the fluid 334 and gas 332may be kept substantially constant (i.e., isothermal). Counterflowheat-exchange fluid 346 at near-ambient pressure may be circulated froma near-ambient-temperature thermal well (not shown) or source (e.g.,waste heat source) or sink (e.g., cold water source) of thermal energy,as described in more detail below.

In various embodiments of the invention, reservoir 320 contains anaqueous foam, either unseparated or partially separated into its gaseousand liquid components. In such embodiments, pump 336 may circulateeither the foam itself, or the separated liquid component of the foam,or both, and recirculation of fluid into reservoir 320 may includeregeneration of foam by apparatus not shown in FIG. 3.

In the energy recovery or expansion mode of operation, a quantity of gasmay be introduced via valve 316 and pipe 312 into the upper chamber 306of cylinder 302 when piston 304 is near or at the top of its stroke(i.e., “top dead center” of cylinder 302). The piston 304 and its rod330 will then be moving downward (the cylinder 302 may be orientedarbitrarily but is shown vertically oriented in this illustrativeembodiment). Heat-exchange fluid 334 may be introduced into chamber 306concurrently via optional pump 350 (alternatively, a pressure drop maybe introduced in line 312 such that pump 350 is not needed) through pipe352 and directional valve 354. This heat-exchange fluid 334 may besprayed into chamber 306 via one or more spray nozzles 356 in such amanner as to generate foam 360. (In some embodiments, foam 360 isintroduced directly into chamber 306 in foam form.) The foam 360 mayentirely fill the entire chamber 306, but is shown in FIG. 3, forillustrative purposes only, as only partially filling chamber 306.Herein, the term “foam” denotes either (a) foam only or (b) any of avariety of mixtures of foam and heat-exchange liquid in other,non-foaming states (e.g., droplets). Moreover, some non-foamed liquid(not shown) may accumulate at the bottom of chamber 306; any such liquidis generally included in references herein to the foam 360 withinchamber 306.

System 300 is instrumented with pressure, piston position, and/ortemperature sensors (not shown) and controlled via control system 362.At a predetermined position of piston 304, an amount of gas 332 andheat-transfer fluid 334 have been admitted into chamber 306 and valve316 and valve 354 are closed. (Valves 316 and 354 may close at the sametime or at different times, as each has a control value based onquantity of fluid desired.) The gas in chamber 306 then undergoes freeexpansion, continuing to drive piston 304 downward. During thisexpansion, in the absence of foam 360, the gas would tend to decreasesubstantially in temperature. With foam 360 largely or entirely fillingthe chamber, the temperature of the gas in chamber 306 and thetemperature of the heat-transfer fluid 360 tend to approximate to eachother via heat exchange. The heat capacity of the liquid component ofthe foam 360 (e.g., water with one or more additives) may be much higherthan that of the gas (e.g., air) such that the temperature of the gasand liquid do not change substantially (i.e., are substantiallyisothermal) even over a many-times gas expansion (e.g., from 250 psig tonear atmospheric pressure, or in other embodiments from 3,000 psig to250 psig).

When the piston 304 reaches the end of its stroke (bottom dead center),the gas within chamber 306 will have expanded to a predetermined lowerpressure (e.g., near atmospheric). Valve 324 will then be opened,allowing gas from chamber 306 to be vented, whether to atmospherethrough pipe 322 and vent 326 (as illustrated here) or, in otherembodiments, to a next stage in the expansion process (e.g., chamber ina separate cylinder), via pipe 322. Valve 324 remains open as the pistonundergoes an upward (i.e., return) stroke, emptying chamber 306. Part orsubstantially all of foam 360 is also forced out of chamber 306 via pipe322. A separator (not shown) or other means such as gravity separationis used to recover heat-transfer fluid, preferably de-foamed (i.e., as asimple liquid with or without additives), and to direct it into astorage reservoir 364 via pipe 366.

When piston 304 reaches top of stroke again, the process repeats withgas 332 and heat-transfer fluid 334 admitted from vessel 320 via valves316 and 354. If additional heat-transfer fluid is needed in reservoir320, it may be pumped back into reservoir 320 from reservoir 364 viapiping 367 and optional pump/motor 368. In one mode of operation, pump368 may be used to continuously refill reservoir 320 such that thepressure in reservoir 320 is held substantially constant. That is, asgas is removed from reservoir 320, heat-transfer fluid 334 is added tomaintain constant pressure in reservoir 320. In other embodiments, pump368 is not used or is used intermittently, the pressure in reservoir 320continues to decrease during an energy-recovery process (i.e., involvingremoval of gas from reservoir 320), and the control system 362 changesthe timing of valves 316 and 354 accordingly so as to reachapproximately the same ending pressure when the piston 304 reaches theend of its stroke. An energy-recovery process may continue until thestorage reservoir 320 is nearly empty of pressurized gas 332, at whichtime an energy-storage process may be used to recharge the storagereservoir 320 with pressurized gas 332. In other embodiments, theenergy-recovery and energy-storage processes are alternated based onoperator requirements.

In either the energy-storage or energy-compression mode of operation,storage reservoir 320 is typically at least partially depleted ofhigh-pressure gas 332, as storage reservoir 320 also typically containsa quantity of heat-transfer fluid 334. Reservoir 364 is at low pressure(e.g., atmospheric or some other low pressure that serves as the intakepressure for the compression phase of cylinder 302) and contains aquantity of heat-transfer fluid 370.

The heat-transfer fluid 370 may be circulated within the reservoir 364via low-power-consumption pump 372. In various embodiments, the fluid370 may be removed from the bottom of the reservoir 364 via piping 367,circulated via pump 372 through a heat exchanger 374, and introduced(e.g., sprayed) back into the top of reservoir 364 via piping 376 andspray head 378 (or other suitable mechanism). By spraying the fluid 370throughout the reservoir gas 380, heat may be added or removed from thegas via the heat-transfer fluid 370. By circulating the heat-transferfluid 370 through heat exchanger 374, the temperature of the fluid 370and gas 380 may be kept near constant (i.e., isothermal). Counterflowheat-exchange fluid 382 at near-ambient pressure may be circulated froma near-ambient-temperature thermal well (not shown) or source (e.g.,waste heat source) or sink (e.g., cold water source) of thermal energy.In one embodiment, counterflow heat-exchange fluid 382 is at hightemperature to increase energy recovery during expansion and/orcounterflow heat-exchange fluid 382 is at low temperature to decreaseenergy usage during compression.

In the energy-storage or compression mode of operation, a quantity oflow-pressure gas is introduced via valve 324 and pipe 322 into the upperchamber 306 of cylinder 302 starting when piston 304 is near top deadcenter of cylinder 302. The low-pressure gas may be from the ambientatmosphere (e.g., may be admitted through vent 326 as illustratedherein) or may be from a source of pressurized gas such as a previouscompression stage. During the intake stroke, the piston 304 and its rod330 will move downward, drawing in gas. Heat-exchange fluid 370 may beintroduced into chamber 306 concurrently via optional pump 384(alternatively, a pressure drop may be introduced in line 386 such thatpump 384 is not needed) through pipe 386 and directional valve 388. Thisheat exchange fluid 370 may be introduced (e.g., sprayed) into chamber306 via one or more spray nozzles 390 in such a manner as to generatefoam 360. This foam 360 may fill the chamber 306 partially or entirelyby the end of the intake stroke; for illustrative purposes only, foam360 is shown in FIG. 3 as only partially filling chamber 306. At the endof the intake stroke, piston 304 reaches the end-of-stroke position(bottom dead center) and chamber 306 is filled with foam 360 generatedfrom air at a low pressure (e.g., atmospheric) and heat-exchange liquid.

At the end of the stroke, with piston 304 at the end-of-stroke position,valve 324 is closed. Valve 388 is also closed, not necessarily at thesame time as valve 324, but after a predetermined amount ofheat-transfer fluid 370 has been admitted, creating foam 360. The amountof heat-transfer fluid 370 may be based upon the volume of air to becompressed, the ratio of compression, and/or the heat capacity of theheat-transfer fluid.

Next, piston 304 and rod 330 are driven upwards via mechanical means(e.g., hydraulic fluid, hydraulic cylinder, mechanical crankshaft) tocompress the gas within chamber 306.

During this compression, in the absence of foam 360, the gas in chamber306 would tend to increase substantially in temperature. With foam 360at least partially filling the chamber, the temperature of the gas inchamber 306 and the temperature of the liquid component of foam 360 willtend to equilibrate via heat exchange. The heat capacity of the fluidcomponent of foam 360 (e.g., water with one or more additives) may bemuch higher than that of the gas (e.g., air) such that the temperatureof the gas and fluid do not change substantially and are near-isothermaleven over a many-times gas compression (e.g., from near atmosphericpressure to 250 psig, or in other embodiments from 250 psig to 3,000psig).

The gas in chamber 306 (which includes, or consists essentially of, thegaseous component of foam 360) is compressed to a suitable pressure,e.g., a pressure approximately equal to the pressure within storagereservoir 320, at which time valve 316 is opened. The foam 360,including both its gaseous and liquid components, is then transferredinto storage reservoir 320 through valve 316 and pipe 312 by continuedupward movement of piston 304 and rod 330.

When piston 304 reaches top of stroke again, the process repeats, withlow-pressure gas and heat-transfer fluid 370 admitted from vent 326 andreservoir 364 via valves 324 and 388. If additional heat-transfer fluidis needed in reservoir 364, it may be returned to reservoir 364 fromreservoir 320 via piping 367 and optional pump/motor 368. Powerrecovered from motor 368 may be used to help drive the mechanicalmechanism for driving piston 304 and rod 330 or may be converted toelectrical power via an electric motor/generator (not shown). In onemode of operation, motor 368 may be run continuously, while reservoir320 is being filled with gas, in such a manner that the pressure inreservoir 320 is held substantially constant. That is, as gas is addedto reservoir 320, heat-transfer fluid 334 is removed from reservoir 320to maintain substantially constant pressure within reservoir 320. Inother embodiments, motor 368 is not used or is used intermittently; thepressure in reservoir 320 continues to increase during an energy-storageprocess and the control system 362 changes the timing of valves 316 and388 accordingly so that the desired ending pressure (e.g., atmospheric)is attained within chamber 306 when the piston 304 reaches bottom ofstroke. An energy-storage process may continue until the storagereservoir 320 is full of pressurized gas 332 at the maximum storagepressure (e.g., 3,000 psig), after which time the system is ready toperform an energy-recovery process. In various embodiments, the systemmay commence an energy-recovery process when the storage reservoir 320is only partly full of pressurized gas 332, whether at the maximumstorage pressure or at some storage pressure intermediate betweenatmospheric pressure and the maximum storage pressure. In otherembodiments, the energy-recovery and energy-storage processes arealternated based on operator requirements.

FIG. 4 depicts an illustrative system 400 that features at least twocylinder assemblies 402, 406 (i.e., an embodiment of assembly 101 inFIG. 1; e.g., cylinder assembly 201 in FIG. 2) and a heat-transfersubsystem 404, 408 (e.g., subsystem 224 in FIG. 2) associated with eachcylinder assembly 402, 406. Additionally, the system includes a thermalwell 410 (e.g., thermal well 242 in FIG. 2) which may be associated witheither or both of the heat-transfer subsystems 404, 408 as indicated bythe dashed lines.

Assembly 402 is in selective fluid communication with a storagereservoir 412 (e.g., 112 in FIG. 1, 222 in FIG. 2) capable of holdingfluid at relatively high pressure (e.g., approximately 3,000 psig).Assembly 406 is in selective fluid communication with assembly 402and/or with optional additional cylinder assemblies between assemblies402 and 406 as indicated by ellipsis marks 422. Assembly 406 is inselective fluid communication with an atmospheric vent 420 (e.g., 120 inFIG. 1, 223 in FIG. 2).

System 400 may compress air at atmospheric pressure (admitted to system400 through the vent 420) stagewise through assemblies 406 and 402 tohigh pressure for storage in reservoir 412. System 400 may also expandair from high pressure in reservoir 412 stagewise through assemblies 402and 406 to a low pressure (e.g., approximately 5 psig) for venting tothe atmosphere through vent 420.

As described in U.S. patent application Ser. No. 13/080,914, filed Apr.6, 2011 (the '914 application), the entire disclosure of which isincorporated by reference herein, in a group of N cylinder assembliesused for expansion or compression of gas between a high pressure (e.g.,approximately 3,000 psig) and a low pressure (e.g., approximately 5psig), the system will contain gas at N−1 pressures intermediate betweenthe high-pressure extreme and the low pressure. Herein each suchintermediate pressure is termed a “mid-pressure.” In illustrative system400, N=2 and N−1=1, so there is one mid-pressure (e.g., approximately250 psig during expansion) in the system 400. In various states ofoperation of the system, mid-pressures may occur in any of the chambersof a series-connected cylinder group (e.g., the cylinders of assemblies402 and 406) and within any valves, piping, and other devices in fluidcommunication with those chambers. In illustrative system 400, themid-pressure, herein denoted “mid-pressure P1,” occurs primarily invalves, piping, and other devices intermediate between assemblies 402and 406.

Assembly 402 is a high-pressure assembly: i.e., assembly 402 may admitgas at high pressure from reservoir 412 to expand the gas tomid-pressure P1 for transfer to assembly 402, and/or may admit gas atmid-pressure P1 from assembly 406 to compress the gas to high pressurefor transfer to reservoir 412. Assembly 406 is a low-pressure assembly:i.e., assembly 406 may admit gas at mid-pressure P1 from assembly 402 toexpand the gas to low pressure for transfer to the vent 420, and/or mayadmit gas at low pressure from vent 420 to compress the gas tomid-pressure P1 for transfer to assembly 402.

In system 400, extended cylinder assembly 402 communicates with extendedcylinder assembly 406 via a mid-pressure assembly 414. Herein, a“mid-pressure assembly” includes or consists essentially of a reservoirof gas that is placed in fluid communication with the valves, piping,chambers, and other components through or into which gas passes. The gasin the reservoir is at approximately at the mid-pressure which theparticular mid-pressure assembly is intended to provide. The reservoiris large enough so that a volume of mid-pressure gas approximately equalto that within the valves, piping, chambers, and other components withwhich the reservoir is in fluid communication may enter or leave thereservoir without substantially changing its pressure. Additionally, themid-pressure assembly may provide pulsation damping, additionalheat-transfer capability, fluid separation, and/or house one or moreheat-transfer sub-systems such as part or all of sub-systems 404 and/or408. As described in the '914 application, a mid-pressure assembly maysubstantially reduce the amount of dead space in various components of asystem employing pneumatic cylinder assemblies, e.g., system 400 in FIG.4. Reduction of dead space tends to increase overall system efficiency.

Alternatively or in conjunction, pipes and valves (not shown in FIG. 4)bypassing mid-pressure assembly 414 may enable fluid to pass directlybetween assembly 402 and assembly 406. Valves 416, 418, 424, and 426control the passage of fluids between the assemblies 402, 406, 412, and414.

A control system 428 (e.g., 122 in FIG. 1, 226 in FIG. 2, 362 in FIG. 3)may control operation of, e.g., all valves of system 400 based onvarious system inputs (e.g., pressure, temperature, piston position,and/or fluid state) from assemblies 402 and 406, mid-pressure assembly414, storage reservoir 412, thermal well 410, heat transfer sub-systems404, 408, and/or the environment surrounding system 420.

It will be clear to persons reasonably familiar with the art ofpneumatic machines that a system similar to system 400 but differing bythe incorporation of one, two or more mid-pressure extended cylinderassemblies may be devised without additional undue experimentation. Itwill also be clear that all remarks herein pertaining to system 400 maybe applied to such an N-cylinder system without substantial revision, asindicated by elliptical marks 422. Such N-cylinder systems, though notdiscussed further herein, are contemplated and within the scope of theinvention. As shown and described in the '678 patent, N appropriatelysized cylinders, where N≧2, may reduce an original (single-cylinder)operating fluid pressure range R to R^(1/N) and correspondingly reducethe range of force acting on each cylinder in the N-cylinder system ascompared to the range of force acting in a single-cylinder system. Thisand other advantages, as set forth in the '678 patent, may be realizedin N-cylinder systems. Additionally, multiple identical cylinders may beadded in parallel and attached to a common or separate drive mechanism(not shown) with the cylinder assemblies 402, 406 as indicated byellipsis marks 432, 436, enabling higher power and air-flow rates.

FIG. 5 is a schematic diagram showing components of a system 500 forachieving approximately isothermal compression and expansion of a gasfor energy storage and recovery using a pneumatic cylinder 502 (shown inpartial cross-section) according to embodiments of the invention. Thecylinder 502 typically contains a slideably disposed piston 504 thatdivides the cylinder 502 into two chambers 506, 508. A reservoir 510contains gas at high pressure (e.g., 3,000 psi); the reservoir 510 mayalso contain a quantity of heat-exchange liquid 512. The heat-exchangeliquid 512 may contain an additive that increases the liquid's tendencyto foam (e.g., by lowering the surface tension of the liquid 512).Additives may include surfactants (e.g., sulfonates), a micro-emulsionof a lubricating fluid such as mineral oil, a solution of agents such asglycols (e.g., propylene glycol), or soluble synthetics (e.g.,ethanolamines). Foaming agents such as sulfonates (e.g., linear alkylbenzene sulfonate such as Bio-Soft D-40 available from Stepan Company ofIllinois) may be added, or commercially available foaming concentratessuch as firefighting foam concentrates (e.g., fluorosurfactant productssuch as those available from ChemGuard of Texas) may be used. Suchadditives tend to reduce liquid surface tension of water and lead tosubstantial foaming when sprayed. Commercially available fluids may beused at an approximately 5% solution in water, such as Mecagreen 127(available from the Condat Corporation of Michigan), which consists inpart of a micro-emulsion of mineral oil, and Quintolubric 807-WP(available from the Quaker Chemical Corporation of Pennsylvania), whichconsists in part of a soluble ethanolamine. Other additives may be usedat higher concentrations (such as at a 50% solution in water), includingCryo-tek 100/Al (available from the Hercules Chemical Company of NewJersey), which consists in part of a propylene glycol. These fluids maybe further modified to enhance foaming while being sprayed and to speeddefoaming when in a reservoir.

A pump 514 and piping 516 may convey the heat-exchange liquid to adevice herein termed a “mixing chamber” (518). Gas from the reservoir510 may also be conveyed (via piping 520) to the mixing chamber 518.Within the mixing chamber 518, a foam-generating mechanism 522 combinesthe gas from the reservoir 510 and the liquid conveyed by piping 516 tocreate foam 524 of a certain grade (i.e., bubble size variance, averagebubble size, void fraction), herein termed Foam A, inside the mixingchamber 518.

The mixing chamber 518 may contain a screen 526 or other mechanism(e.g., source of ultrasound) to vary or homogenize foam structure.Screen 526 may be located, e.g., at or near the exit of mixing chamber518. Foam that has passed through the screen 526 may have a differentbubble size and other characteristics from Foam A and is herein termedFoam B (528). In other embodiments, the screen 526 is omitted, so thatFoam A is transferred without deliberate alteration to chamber 506.

The exit of the mixing chamber 518 is connected by piping 530 to a portin the cylinder 502 that is gated by a valve 532 (e.g., a poppet-stylevalve) that permits fluid from piping 530 to enter the upper chamber(air chamber) 506 of the cylinder 502. Valves (not shown) may controlthe flow of gas from the reservoir 510 through piping 520 to the mixingchamber 518, and from the mixing chamber 518 through piping 528 to theupper chamber 506 of the cylinder 502. Another valve 534 (e.g., apoppet-style valve) permits the upper chamber 506 to communicate withother components of the system 500, e.g., an additional separator device(not shown), the upper chamber of another cylinder (not shown), or avent to the ambient atmosphere (not shown).

The volume of reservoir 510 may be large (e.g., at least approximatelyfour times larger) relative to the volume of the mixing chamber 518 andcylinder 502. Foam A and Foam B are preferably statically stable foamsover a portion or all of the time-scale of typical cyclic operation ofsystem 500: e.g., for a 120 RPM system (i.e., 0.5 seconds perrevolution), the foam may remain substantially unchanged (e.g., lessthan 10% drainage) after 5.5 seconds or a time approximately five timesgreater than the revolution time.

In an initial state of operation of a procedure whereby gas stored inthe reservoir 510 is expanded to release energy, the valve 532 is open,the valve 534 is closed, and the piston 504 is near top dead center ofcylinder 502 (i.e., toward the top of the cylinder 502). Gas from thereservoir 510 is allowed to flow through piping 520 to the mixingchamber 518 while liquid from the reservoir 510 is pumped by pump 514 tothe mixing chamber 518. The gas and liquid thus conveyed to the mixingchamber 518 are combined by the foam-generating mechanism 522 to formFoam A (524), which partly or substantially fills the main chamber ofthe mixing chamber 518. Exiting the mixing chamber 518, Foam A passesthrough the screen 526, being altered thereby to Foam B. Foam B, whichis at approximately the same pressure as the gas stored in reservoir510, passes through valve 532 into chamber 506. In chamber 506, Foam Bexerts a force on the piston 504 that may be communicated to a mechanism(e.g., an electric generator, not shown) external to the cylinder 502 bya rod 536 that is connected to piston 504 and that passes slideablythrough the lower end cap of the cylinder 502.

The gas component of the foam in chamber 506 expands as the piston 504and rod 536 move downward. At some point in the downward motion ofpiston 504, the flow of gas from reservoir 510 into the mixing chamber518 and thence (as the gas component of Foam B) into chamber 506 may beended by appropriate operation of valves (not shown). As the gascomponent of the foam in chamber 506 expands, it will tend, unless heatis transferred to it, to decrease in temperature according to the IdealGas Law; however, if the liquid component of the foam in chamber 506 isat a higher temperature than the gas component of the foam in chamber506, heat will tend to be transferred from the liquid component to thegas component. Therefore, the temperature of the gas component of thefoam within chamber 506 will tend to remain constant (approximatelyisothermal) as the gas component expands.

When the piston 504 approaches bottom dead center of cylinder 502 (i.e.,has moved down to approximately its limit of motion), valve 532 may beclosed and valve 534 may be opened, allowing the expanded gas in chamber506 to pass from cylinder 502 to some other component of the system 500,e.g., a vent or a chamber of another cylinder for further expansion.

In some embodiments, pump 514 is a variable-speed pump, i.e., may beoperated so as to transfer liquid 512 at a slower or faster rate fromthe reservoir 510 to the foam-generating mechanism 522 and may beresponsive to signals from the control system (not shown). If the rateat which liquid 512 is transferred by the pump 514 to the foam-mechanism522 is increased relative to the rate at which gas is conveyed fromreservoir 510 through piping 520 to the mechanism 522, the void fractionof the foam produced by the mechanism 522 may be decreased. If the foamgenerated by the mechanism 522 (Foam A) has a relatively low voidfraction, the foam conveyed to chamber 506 (Foam B) will generally alsotend to have a relatively low void fraction. When the void fraction of afoam is lower, more of the foam consists of liquid, so more thermalenergy may be exchanged between the gas component of the foam and theliquid component of the foam before the gas and liquid components comeinto thermal equilibrium with each other (i.e., cease to change inrelative temperature). When gas at relatively high density (e.g.,ambient temperature, high pressure) is being transferred from thereservoir 510 to chamber 506, it may be advantageous to generate foamhaving a lower void fraction, enabling the liquid fraction of the foamto exchange a correspondingly larger quantity of thermal energy with thegas fraction of the foam.

All pumps shown in subsequent figures herein may also be variable-speedpumps and may be controlled based on signals from the control system.Signals from the control system may be based on system-performance(e.g., gas temperature and/or pressure, cycle time, etc.) measurementsfrom one or more previous cycles of compression and/or expansion.

Embodiments of the invention increase the efficiency of a system 500 forthe storage and retrieval of energy using compressed gas by enabling thesurface area of a given quantity of heat-exchange liquid 512 to begreatly increased (with correspondingly accelerated heat transferbetween liquid 512 and gas undergoing expansion or compression withincylinder 502) with less investment of energy than would be required byalternative methods of increasing the surface of area of the liquid,e.g., the conversion of the liquid 512 to a spray.

In other embodiments, the reservoir 510 is a separator rather than ahigh-pressure storage reservoir as depicted in FIG. 5. In suchembodiments, piping, valves, and other components not shown in FIG. 5are supplied that allow the separator to be placed in fluidcommunication with a high-pressure gas storage reservoir as well as withthe mixing chamber 518. An arrangement of this type will be shown in anddescribed with reference to FIG. 9.

FIG. 6 is a schematic diagram showing components of a system 600 forachieving approximately isothermal compression and expansion of a gasfor energy storage and recovery using a pneumatic cylinder 604 (shown inpartial cross-section) according to embodiments of the invention. System600 is similar to system 500 in FIG. 5, except that system 600 includesa bypass pipe 638. Moreover, two valves 640, 642 are explicitly depictedin FIG. 6. Bypass pipe 638 may be employed as follows: (1) when gas isbeing released from the storage reservoir 610, mixed with heat-exchangeliquid 612 in the mixing chamber 618, and conveyed to chamber 606 ofcylinder 604 to be expanded therein, valve 640 will be closed and valve642 open; (2) when gas has been compressed in chamber 606 of cylinder604 and is to be conveyed to the reservoir 610 for storage, valve 640will be open and valve 642 closed. Less friction will tend to beencountered by fluids passing through valve 640 and bypass pipe 638 thanby fluids passing through valve 642 and screen 626 and around thefoam-generating mechanism 622. In other embodiments, valve 642 isomitted, allowing fluid to be routed through the bypass pipe 638 by thehigher resistance presented by the mixing chamber 618, and valve 640 isa check valve preventing fluid flow when gas is being released inexpansion mode. The direction of fluid flow from chamber 606 to thereservoir 610 via a lower-resistance pathway (i.e., the bypass pipe 638)will tend to result in lower frictional losses during such flow andtherefore higher efficiency for system 600.

In other embodiments, the reservoir 610 is a separator rather than ahigh-pressure storage reservoir as depicted in FIG. 6. In suchembodiments, piping, valves, and other components not shown in FIG. 6are supplied that allow the separator to be placed in fluidcommunication with a high-pressure gas storage reservoir as well as withthe mixing chamber 618 and bypass pipe 638.

FIG. 7 is a schematic diagram showing components of a system 700 forachieving approximately isothermal compression and expansion of a gasfor energy storage and recovery using a pneumatic cylinder 702 (shown inpartial cross-section) according to embodiments of the invention. System700 is similar to system 500 in FIG. 5, except that system 700 omits themixing chamber 518 and instead generates foam inside the storagereservoir 710. In system 700, a pump 714 circulates heat-exchange liquid712 to a foam-generating mechanism 722 (e.g., one or more spray nozzles)inside the reservoir 710. The reservoir 710 may, by means of the pump714 and mechanism 722, be filled partly or entirely by foam of aninitial or original character, Foam A (724). The reservoir 710 may beplaced in fluid communication via pipe 720 with a valve-gated port 744in cylinder 702. Valves (not shown) may govern the flow of fluid throughpipe 720. An optional screen 726 (or other suitable mechanism such as anultrasound source), shown in FIG. 7 inside pipe 720 but locatableanywhere in the path of fluid flow between reservoir 710 and chamber 706of the cylinder 702, serves to alter Foam A (724) to Foam B (728),regulating characteristics such as bubble-size variance and averagebubble size.

In other embodiments, the reservoir 710 is a separator rather than ahigh-pressure storage reservoir as depicted in FIG. 7. In suchembodiments, piping, valves, and other components not shown in FIG. 7will be supplied that allow the separator to be placed in fluidcommunication with a high-pressure gas storage reservoir as well as withthe cylinder 702. In other embodiments, a bypass pipe similar to thatdepicted in FIG. 6 is added to system 700 in order to allow fluid topass from cylinder 702 to reservoir 710 without passing through thescreen 726.

FIG. 8 is a schematic diagram showing components of a system 800 forachieving approximately isothermal compression and expansion of a gasfor energy storage and recovery using a pneumatic cylinder 802 (shown inpartial cross-section) according to embodiments of the invention. System800 is similar to system 500 in FIG. 5, except that system 800 omits themixing chamber 518 and instead generates foam inside the air chamber 806of the cylinder 802. In system 800, a pump 814 circulates heat-exchangeliquid 812 to a foam-generating mechanism 822 (e.g., one or more spraynozzles injecting into cylinder and/or onto a screen through whichadmitted air passes) either located within, or communicating with (e.g.,through a port), chamber 806. The chamber 806 may, by means of the pump814 and mechanism 822 (and by means of gas supplied from reservoir 810via pipe 820 through a port 844), be filled partly or substantiallyentirely by foam. The reservoir 810 may be placed in fluid communicationvia pipe 820 with valve-gated port 844 in cylinder 802. Valves (notshown) may govern the flow of fluid through pipe 820.

FIG. 9 is a schematic diagram showing components of a system forachieving approximately isothermal compression and expansion of a gasfor energy storage and recovery using two pneumatic cylinder stages 902,904 (shown in partial cross-section) according to embodiments of theinvention. The higher-pressure cylinder 902 may be placed in fluidcommunication with a first separator 906 and/or a second separator 908;the lower-pressure cylinder 902 may be placed in fluid communicationwith the second separator 908 and/or a third separator 910. The firstseparator 906 may be placed in fluid communication with a high-pressuregas storage reservoir (not shown). The third separator 910 may be placedin fluid communication with a vent (not shown) that allows air to beexchanged with the environment. Fluid passing between the firstseparator 906 and the high-pressure cylinder 902, or between thehigh-pressure cylinder 902 and the second separator 908, or between thesecond separator 908 and the low-pressure cylinder 904, or between thelow-pressure cylinder 904 and the third separator 910, may be routedthrough mixing chambers 912, 914, 916, 918 or bypass pipes 920, 922,924, 926. Arrangements for controlling fluid communication between thehigh-pressure reservoir, the vent, the cylinders 902, 904, the mixingchambers 912, 914, 916, 918, and the bypass pipes 920, 922, 924, 926 mayinclude valves, piping, and other components not depicted in FIG. 9. Invarious embodiments, the bypass pipes 920, 922, 924, 926, and/oradditional bypass pipes not depicted in FIG. 9 may allow fluid to bypassthe separators 906, 908, 910.

During expansion of gas from storage, gas may first be partly expandedin a high-pressure cylinder 902, allowing some of its potential elasticenergy to be recovered by mechanisms (not shown) external to thecylinder 902, and then further expanded in the low-pressure cylinder904, allowing most or substantially all of the remainder of itspotential elastic energy to be recovered. During compression of gas forstorage, gas may be partly compressed in the lower-pressure cylinder 904and then further compressed in the higher-pressure cylinder 902.

The system 900 includes arrangements similar to those depicted in FIG. 5and/or FIG. 6 for achieving approximately isothermal compression andexpansion of gas using foam to facilitate heat exchange between the gasand a heat-exchange liquid.

Each of the three separators (e.g., the first separator 906) may containbaffles (e.g., baffle 928) or other internal mechanisms for encouragingthe breakdown or separation of a fluid foam into its gas and liquidcomponents. Other techniques (not shown), such as spraying into the foamor mechanical shearing the foam, may be employed to encourage foamdegradation in a separator. Separated liquid 930, 932, 934 may beconveyed by pumps 936, 938, 940, 942 to the mixing chambers 912, 914,916, 918 (which preferably have integral screens) to be used in theformation of fresh foam.

Valves 944, 946, 948, 950, 952, 954, 956, 958 may be used to directliquid passing between the separators 906, 908, 910 and the cylinders902, 904 either through the mixing chambers 912, 914, 916, 918 or thebypass pipes 920, 922, 924, 926. In cylinders 902, 904, valves 964, 966,968, and 970 (e.g., poppet-type valves) control the ingress and egressof fluids. Preferably, the pumps 936, 938, 940, 942 run only when foamis to be generated in their respective mixing chambers 912, 914, 916,918.

In general, gas that is to conveyed to an air chamber 960, 962 of acylinder 902, 904, there to be either expanded or compressed, is routedthrough a mixing chamber in order to be foamed with heat-exchangeliquid, enabling heat exchange to occur between the liquid and the gasduring expansion or compression for the purpose of approximating anisothermal process.

In an initial state of operation of a procedure whereby gas stored inthe high-pressure reservoir (not shown) is expanded in system 900 torelease energy, piston 972 of the high-pressure cylinder 902 may beapproximately at top dead center, piston 974 of the low-pressurecylinder 904 may be at bottom dead center (although the relative pistonpositions 972 and 974 may be arbitrarily phased), and the upper chamber962 of the lower-pressure cylinder 904 is wholly or partly filled withfoam at low pressure; in expansion mode, optional bypass valves 944 and952 are closed and optional bypass valves 948 and 956 are open, allowingflow through mixing chambers 912 and 916 and optional valves 946 and954, but bypassing flow through mixing chambers 914 and 918 by theclosing of optional valves 950 and 958. Gas at high pressure ispermitted to flow from the high-pressure reservoir, through theseparator 906, and into the mixing chamber 912, where it is combinedwith heat-exchange liquid 930 to form foam. This foam, after optionallypassing through a screen internal to the mixing chamber 912, flowsthrough valve 946 and valve 964 into chamber 960 of the high-pressurecylinder 902, which it partly or substantially fills. In chamber 960,the foam exerts a force on the piston 972 that may be communicated to amechanism external to the cylinder 902.

The gas component of the foam in chamber 960 expands as the piston 972moves downward. At some point in the downward motion of piston 972, theflow of gas from the storage reservoir, through the separator 906, intothe mixing chamber 912, and thence (as the gas component of the foam)into chamber 960 may be ended by closure of valve 964. As in theexpanding foam in the cylinder of system 500 in FIG. 5, the temperatureof the gas component of the foam within chamber 960 will tend to remainconstant (approximately isothermal) as the gas component expands.

The piston 974 of the low-pressure cylinder 904 may be moved upward frombottom dead center concurrently with the downward motion of piston 972described above, expelling the low-pressure foam within chamber 962through the bypass valve 956 and pipe 926 into the separator 910. In theseparator 910, the liquid component of the foam settles and accumulatesas a body of liquid 934. The gas component of the foam passing fromchamber 962 to the separator 910 proceeds out of the separator to theexternal vent (not shown) and is released to the environment. Additionalmechanisms (not shown) for speeding the settling time of the foam intoseparate liquid and air, and for removing liquid from the venting air,may also be included. In brief, the high-pressure cylinder 902 mayperform an intake stroke while the low-pressure cylinder 904 performs anexhaust stroke.

When the piston 972 of the high-pressure cylinder 902 has reached bottomdead center of cylinder 902 and the piston 974 has reached top deadcenter of the low-pressure cylinder 904, the chamber 960 of thehigh-pressure cylinder 902 contains gas at a mid-pressure (e.g., 300psi). Subsequently valve 966 may be opened, and the piston 972 of thehigh-pressure cylinder 902 may begin to move upward, and valve 968 maybe opened and the piston 974 of the low-pressure cylinder 904 may beginto move downward. Concurrently, the pump 940 runs, conveyingheat-exchange liquid 932 to the mixing chamber 916 to be foamed. Underthese conditions, gas at mid-pressure flows from the chamber 960 of thehigh-pressure cylinder 902, through the bypass pipe 922 and into theseparator 908. While the cylinders 902 and 904 do not need to beout-of-phase, in an out-of-phase scenario, mid-pressure gas flows fromthe separator 908 through the mixing chamber 916, and (foamed withheat-exchange liquid) into chamber 962 of the low-pressure cylinder 904,where it performs work on the piston 974 that is moving downward. Inbrief, the high-pressure cylinder 902 may perform an exhaust strokewhile the low-pressure cylinder 904 performs an intake stroke.

It will be clear to persons reasonably familiar with the art ofpneumatic and hydraulic machines that the series of operations describedabove may be repeated cyclically, expanding any desired quantity of gasfrom storage in an approximately isothermal manner. It will also beclear that the system 900 may assume a series of states of operationthat isothermally compress gas admitted through the vent and deliver thecompressed gas to the high-pressure storage reservoir, and that thisseries of states may also be repeated cyclically, compressing anydesired quantity of gas into storage. Such operations (as well as thosedescribed in connection with FIG. 9) may be performed via larger numbersof cylinders; multiple cylinders may expand or compress gas in parallel,or three or more stages (each of one or more cylinders) may be utilizedto serially expand or compress gas.

In general, during both compression and expansion, system 900 may beoperated so that fluids being exhausted from cylinders will be routedthrough the bypass tubes 920, 922, 924, 926, and fluids being taken inby cylinders will be routed through the mixing chambers 912, 914, 916,918 in order that foams may be admitted to the air chambers 960, 962.Moreover, the screens (or other suitable foam-altering mechanisms)internal to the mixing chambers 912, 914, 916, 918 and the pumps 936,938, 940, 942 may be operated in a manner that optimizes the efficiencyof system 900 (e.g., continuous flow at a minimal pressure drop). Mixingchambers may be used for fine droplet spray as opposed to foam mixing insome or all of the mixing chambers, e.g., the low pressure chamber 918may be used to suspend a mist of small droplets (e.g., 100 micron meandiameter or smaller) within the air in the chamber, whereas the otherchambers 912, 914, 916 may be used to generate a suspension of aqueousfoam. Some or all of the mixing chambers 912, 914, 916, 918 may bereplaced with direct injection into the cylinder as shown in FIG. 8.Some or all of the direct-injection foam generators (e.g., 822 in FIG.8) may be replaced with direct-injection spray generators such as anarray of nozzles, e.g., a direct-injection mechanism (not shown) in thelow pressure cylinder 904 may be used to suspend a mist of smalldroplets (e.g., 100-micron mean diameter or smaller) whereas adirect-injection mechanism (not shown) in the high pressure cylinder 902may be used to generate an aqueous foam. Cylinders 902 and/or 904 mayhave two direct-injection mechanisms, one for compression and one forexpansion, and one such mechanism may be for spray and one for foamgeneration.

FIG. 10 is a plot of experimental data on the isothermal efficiency of agas-expansion process using a spray of tap water without foamingadditives. All expansions plotted in FIG. 10 began at 3,000 psig andended at 250 psig and took place in a 10-gallon cylinder with an 8-inchinterior diameter and a 52-inch stroke length. Each symbol (i.e.,circle, triangle, or square) plots the isothermal efficiency of a singlerun of the energy-conversion system incorporating the cylinder.Expansions at three different rates of output power (37 kW, 50 kW, and70 kW) are plotted in FIG. 10. The vertical axis corresponds toisothermal efficiency of expansion, i.e., the fraction of the energythat is extracted during a single actual expansion compared with theenergy theoretically extractable from a given quantity of gas viaisothermal expansion. Expansions that decrease in temperature generallyyield less energy than an ideal isothermal expansion and thus result inless than 100% isothermal efficiency. For example, an adiabaticexpansion over the same pressure range would result in approximately 50%of the energy of an ideal isothermal expansion, and thus haveapproximately 50% isothermal efficiency.

In the expansions for which isothermal efficiency is plotted in FIG. 10,the heat-exchange spray commences at the beginning of expansion and isstopped when the expanding gas reaches a predetermined thresholdpressure or “spray end pressure.” The horizontal axis of FIG. 10corresponds to this spray end pressure. Since the beginning gaspressures are the same for all expansions in FIG. 10, lower pressurestend to be attained within the cylinder at later times; thus, for eachoutput power level, lower spray end pressure (leftward on horizontalaxis) typically corresponds to a longer period of spraying (increasedspray time).

As FIG. 10 shows, and as the arrow labeled “Increasing spray time”highlights, there is a clear tendency, for this experimental setup, andusing tap water without foaming additive as a heat-exchange sprayliquid, for efficiency to decrease with spray end pressure (i.e., toincrease with spray time). Without limiting the scope of the presentinvention, it is believed that this trend occurs because heat transferbetween the heat-exchange liquid and the gas within the cylinder occursat a significant rate only while the liquid and gas are in contact witheach other over a large surface area. For a non-foaming spray, theliquid and gas are in contact over a large surface area only while thespray is being generated and the droplets are falling through the gas.Heat exchange slows greatly soon after the spray ceases to be generated.Spraying throughout the whole expansion or most of the expansiontherefore allows closer approximation to an isothermal expansion andthus higher isothermal efficiency.

FIG. 11 is a plot of experimental data on the isothermal efficiency of agas-expansion process using a spray of tap water with 2.5% by volume ofa foaming additive (which in this exemplary experiment includes, atleast in part, an ethanolamine). The axes of the plot are as describedabove for FIG. 10. Expansions at two different rates of output power (50kW and 70 kW) are plotted in FIG. 11.

As FIG. 11 shows, and as the arrow labeled “Increasing spray time”highlights, there is, if any, a slight tendency, at least for thisexperimental setup and using tap water with 2.5% foaming additive as aheat-exchange spray liquid, for efficiency to increase with spray endpressure (i.e., to decrease with spray time). Furthermore, theisothermal efficiencies obtained utilizing foaming heat-exchange spraystend to be higher than those obtained with non-foaming sprays (FIG. 10).Without limiting the scope of the present invention, it is believed thatthe physical basis of this trend is that for a foaming spray, the liquidand gas are in contact over a large surface area not only while thespray is being actively generated, but for as long as the resultingliquid-gas mixture persists substantially as a foam within the cylinder.Significant heat exchange thus may continue after the spray ceases to begenerated. For the 2.5% water-plus-additive mixture used in theexperiments whose results are plotted in FIG. 11, the entire volume ofthe expansion chamber within the cylinder is filled with foam soon(i.e., a small fraction of the duration of the expansion stroke) afterthe commencement of spraying. Longer spray times (lower spray endpressures) may be associated with lower isothermal efficiencies becausethey consume additional energy while producing relatively littleadditional heat transfer. Thus, under the experimental conditionspertaining to the data plotted in FIG. 11, the highest-efficiency cycleis achieved with the shortest period of spraying. Notably, the highestefficiency attained under the conditions illustrated in FIG. 11(approximately 97%) is higher than the highest efficiency attained underthe conditions illustrated in FIG. 10, i.e., with non-foaming spray(approximately 95.6%). With larger or smaller concentrations of one ormore foaming additives (e.g., additives other than that utilized in thisexemplary embodiment), other trends may be observed: e.g., at very lowadditive concentrations, foaming may be so slight as to not produce theeffects observed with 2.5% concentration, in which case data moreclosely resembling those of FIG. 10 may be obtained.

FIG. 12 is a plot of experimental data on the isothermal efficiency of agas-compression process using a spray of tap water without foamingadditives. All compressions plotted in FIG. 12 began at 250 psig andended at 3,000 psig and took place in a 10-gallon cylinder with an8-inch interior diameter and a 52-inch stroke length. Each symbol (i.e.,diamond, square, or triangle) plots the isothermal efficiency of asingle run of the energy-conversion system. Compressions at threedifferent rates of output power (37 kW, 50 kW, and 70 kW) are plotted inFIG. 12. The vertical axis corresponds to isothermal efficiency ofcompression, i.e., the fraction of the energy that is required tocompress a given quantity of gas to a certain volume (from a givenstarting pressure and volume) via isothermal compression compared withthe actual measured energy to compress that same quantity of gas to thesame volume. Compressions that increase in temperature generally requiremore energy than an ideal isothermal compression and thus result in lessthan 100% isothermal efficiency. For example, an adiabatic compressionof 10 gallons of 250 psig gas to a volume of 2 gallons would typicallyrequire approximately 170% of the energy of an ideal isothermalcompression to the same volume, and thus have approximately 60% (i.e.,100/170) isothermal efficiency.

In the compressions for which isothermal efficiency is plotted in FIG.12, the heat-exchange spray commences at the beginning of compressionand is stopped at some predetermined threshold pressure or “spray endpressure.” The horizontal axis of FIG. 12 represents this spray endpressure. Since the beginning and end gas pressures are the same for allexpansions in FIG. 12, lower pressures are attained within the cylinderat earlier times; thus, lower spray end pressure (leftward on horizontalaxis) corresponds to a shorter period of spraying (decreased spraytime).

As the data plotted in FIG. 12 show, and the arrow labeled “Increasingspray time” highlights, there is a tendency, using tap water withoutfoaming additives as a heat-exchange spray liquid, for efficiency toincrease with spray end pressure (i.e., to increase with spray time) upto a spray pressure of about 2,000 psi. Without limiting the scope ofthe present invention, it is believed that the physical basis of thistrend is that heat transfer between the heat-exchange liquid and the gaswithin the cylinder occurs at a significant rate only while the liquidand gas are in contact over a large surface area. For a non-foamingspray, the liquid and gas are typically in contact over a large surfacearea only while the spray is being generated and its droplets arefalling through the gas. Significant heat exchange ceases soon after thespray ceases to be generated. Spraying throughout the whole compression(or, for the compressions plotted in FIG. 12, most of the compression)allows closer approximation to an isothermal compression and thus higherisothermal efficiency.

FIG. 13 is a plot of experimental data on the isothermal efficiency of agas-compression process using a spray of tap water with 2.5% by volumeof foaming additives (i.e., the same foaming additives utilized togenerate the data of FIG. 11). The axes of the plot are as describedabove for FIGS. 10, 11, and 12. Compressions at two different rates ofoutput (50 kW and 70 kW) are plotted in FIG. 13.

As the data plot in FIG. 13 shows, and the arrow labeled “Increasingspray time” highlights, isothermal compression efficiency isapproximately independent of spray end pressure using tap water with2.5% foaming additives as a heat-exchange spray liquid in thisexperimental system. Without limiting the scope of the presentinvention, it is believed that the physical basis of this independenceis that for a foaming spray, the liquid and gas are in contact over alarge surface area not only while the spray is being generated, but foras long as the liquid-gas mixture persists in the form of a foam withinthe cylinder. Significant heat exchange thus continues after the sprayceases to be generated. For the 2.5% mixture utilized in the experimentswhose results are plotted in FIG. 13, the entire volume of the expansionchamber within the cylinder is filled with foam soon (i.e., a smallfraction of the stroke) after the commencement of spraying. Under theexperimental conditions illustrated in FIG. 13, the highest-efficiencycycle is achieved with the shortest period of spraying, as well as withthe longest. Notably, the highest efficiency attained under theconditions illustrated in FIG. 13 (over 98%) is significantly higherthan the highest efficiency attained under the conditions illustrated inFIG. 12, non-foaming spray (approximately 96%). With larger or smallerconcentration of one or more foaming additives, other trends may beobserved: e.g., at very low concentrations (or other concentrations ofother additives), foaming may be so slight as to not produce the effectsobserved with 2.5% concentration, in which case data more closelyresembling of FIG. 12 may be obtained.

Achieving high isothermal efficiency by using foaming spray liquid withrelatively short spray time has the advantage that the parasitic energydevoted to spray generation is reduced relative to a more prolongedspraying period. During compressions, a short, initial period ofspraying in general must overcome low gas pressure in the cylinderchamber being sprayed compared to the pressure in later parts of thecompression, which also saves spraying energy. During expansions, whenwater warmer than the gas in the chamber is generally sprayed to achieveisothermal expansion, spraying when the gas is at the initial pressurerequires only a small pressure increase for water at that initialpressure (e.g., water in the storage reservoir 320 in FIG. 3) and thus alow pumping power; whereas if water is sprayed from that initialpressure (e.g., the storage-reservoir pressure) into a much lowercylinder pressure, energy may be lost in the throttling of fluid duringthe spraying process. Additives that produce foaming may simultaneouslyproduce one or more other benefits, such as increasing lubricity orpreventing corrosion.

Other considerations in the energy-efficient generation of foam are (1)whether, to minimize energy lost in circulation of liquids acrosspressure differentials, foam should be generated before admission to theair chamber of a pneumatic cylinder for compression or expansion (hereintermed the “pre-foam” or “port injection” approach), or directly intothe air chamber of the pneumatic cylinder (herein termed the“foam-during” or “direct injection” approach), and (2) what theliquid-to-gas mass ratio of the foam should be to optimize heatexchange, pumping energy, and other efficiency considerations. Theillustrative systems shown in FIG. 5, FIG. 6, and FIG. 7 are pre-foamsystems; the illustrative systems shown in FIG. 8 is a foam-duringsystem.

FIG. 14 is an illustrative graph of calculated energy expended in thegeneration and injection of foam or foaming liquid into the air chamberof a pneumatic cylinder as a function of time, comparing the pre-foamapproach to the foam-during approach. By basic principles of hydraulics,the foaming energy W_(foam) (i.e., where mechanical agitation isemployed to induce foaming, the energy required to produce a givenamount of foam by forcing foaming liquid through a device that minglesthe liquid with gas to form a foam) is determined by the volume offoamed liquid V_(liquid) multiplied by the change in pressureΔP_(foaming) undergone by the foamed liquid in its passage through thefoaming device: W_(foam)=V_(liquid)×ΔP_(foaming). Where V_(liquid) andΔP_(foaming) vary with time, total foaming energy W_(foam) over a giventime interval is given by the integral of V_(liquid)×ΔP_(foaming) overthat interval: W_(foam)=∫V_(liquid)×ΔP_(foaming) dt (where the limits ofintegration are not explicitly indicated). If V_(liquid) is constant andΔP_(foaming) varies with time, W_(foam)=V_(liquid)×∫ΔP_(foaming) dt. Fora given gas-to-liquid mass ratio for a given quantity of gas, V_(liquid)is fixed; therefore, to minimize W_(foam), average ΔP_(foaming) must beminimized.

In general, for the foam-during (i.e., direct-injection) approach,ΔP_(foaming) varies throughout a piston stroke within a cylinderassembly, as ΔP_(foaming) is given by the difference between the sourcepressure of the foaming liquid and the pressure of the gas into whichthe foaming liquid is injected. The pressure of the source of foamingliquid is in general approximately constant, while the pressure of a gasundergoing compression or expansion within a cylinder assembly changessubstantially. Creation of a foam within a cylinder assembly during,e.g., a compression stroke, thus entails forcing foaming liquid into theair chamber of the cylinder assembly against an increasing pressuredifference (increasing ΔP_(foaming)).

In the graph in FIG. 14, the vertical axis, “Differential SprayPressure,” corresponds to ΔP_(foaming) and the horizontal axiscorresponds to time. The area under a curve plotting ΔP_(foaming) versustime is ∫ΔP_(foaming) dt. Therefore, sinceW_(foam)=V_(liquid)×∫ΔP_(foaming) dt, if V_(liquid) is presumedconstant, foaming energy W_(foam) for a given gas expansion orcompression process will be proportional to the area under theΔP_(foaming) versus time curve for that process.

The solid line in the graph in FIG. 14 shows ΔP_(foaming) for afoam-during (i.e., direct-injection) compression of a quantity of gasbeginning at approximately 0 psig. As the pressure within the airchamber of the cylinder assembly increases, ΔP_(foaming) increases(rising curve in graph). If foam creation continues during a period oftime after compression is complete, ΔP_(foaming) will be approximatelyconstant for that period of time (flat portion of solid curve in graphfrom time equals approximately 0.8 unit to time equals 1.0 unit). Thearea under the solid line in the graph in FIG. 14 is ∫ΔP_(foaming) dt;therefore, by W_(foam)=V_(liquid)×∫ΔP_(foaming) dt, foaming energyW_(foam) for this illustrative compression process is proportional tothe area under the solid line.

Similarly, the dotted line in the graph in FIG. 14 shows ΔP_(foaming)for a pre-foam (i.e., port-injection) compression of a quantity of gasbeginning at approximately 0 psig. The quantity of gas and otherfeatures of the compression process are the same as those for thecompression represented by the solid line in the graph. In the pre-foamprocess, foam is generated at low pressure as the gas to be compressedis admitted into the air chamber of cylinder assembly. ΔP_(foaming) islow and constant throughout foam generation (horizontal dotted line inthe graph) for the pre-foam process. Manifestly, the area under thedotted line in the graph (i.e., ∫ΔP_(foaming) dt, which equals thefoaming energy W_(foam) for this illustrative pre-foam compressionprocess) is smaller than the area under the solid line in the graph.Therefore, foaming energy W_(foam) is smaller for a pre-foam compressionprocess than for a comparable foam-during compression process.

For a pre-foam process in which foam is created in a foam generatorexternal to the cylinder assembly (as, e.g., in FIG. 5), the generatedfoam must be admitted through a valve (e.g., a poppet valve) into theair chamber of the cylinder assembly. During either expansion orcompression, passage through the valve into the cylinder assembly willentail some pressure drop for the foam and therefore some energy loss.However, the pressure drop through a valve (e.g., poppet valve)governing the entrance or exit of fluid from the air chamber of thecylinder assembly will generally be lower than the pressure drop througha foam-generating device. Therefore, pre-foam processes will in generalrealize lower energy losses, and thus higher efficiency, thanfoam-during processes.

Moreover, for a spray-during process, either of compression orexpansion, foam generation must occur in episodes or time intervalswhose duration and timing are determined by the action of the cylinderassembly. For a pre-spray process, foam may be generated or regeneratedcontinuously (e.g., within a large foam generator or a reservoirattached to the foam generator), not only during each compression orexpansion stroke of the cylinder assembly. Performing foam generationover a longer time period is likely to further lower ΔP_(foaming)compared to more rapid foaming, allowing further efficiency gains to berealized.

The graph in FIG. 15 plots calculated temperature changes of the liquidcomponent of a foam undergoing a set of illustrative compressionprocesses for a range of foam mass ratios and a set of illustrativecompression processes. The vertical axis of the graph in FIG. 15corresponds to the temperature change of the liquid component of a foamundergoing compression, and the horizontal axis of the graph correspondsto the mass ratio of the foam undergoing compression, i.e., the ratio ofthe mass of liquid m_(w) per unit volume of foam to the mass of gasm_(a) per unit volume of foam. (The mass ratio m_(w)/m_(a) does not varywith pressure, except as some fraction of the gas component may dissolveinto or evaporate from the liquid component, altering m_(a), or as somefraction of the liquid component may evaporate into or condense out ofthe gas component, altering m_(w). The illustrative graph in FIG. 15neglects the effects of dissolved gas and vapor-liquid phase changes ofthe liquid component, as these are relatively minor effects.)

When a foam including or consisting essentially of a compressible gasand an approximately incompressible liquid is compressed, the change involume of the foam is due to the compression of the gas component. Asnoted earlier, gas undergoing compression tends to heat. The risingtemperature of the gas component of a foam undergoing compression willcause thermal energy to be transferred to the liquid component of thefoam. The larger the mass ratio m_(w)/m_(a), the greater the mass ofliquid available to absorb thermal energy for each mass unit of gas, andthe lower the resulting change in temperature T of the liquid for agiven overall change in pressure of the foam. Final T of the liquid isin general a function of initial foam temperature, the heat transfercoefficients of the gas and liquid components of the foam, the heatcapacity of the gas and of the liquid, the foam mass ratio, the foamstart pressure, and the foam end pressure. In the graph in FIG. 15, onlymass ratio and foam end pressure vary.

The change in temperature (ΔT) of the liquid component of a variety ofhypothetical foams undergoing compression is represented by the seriesof curves in the graph in FIG. 15. Compressions are shown for alow-pressure cylinder (LP) and a second-stage high-pressure cylinder(HP). For the LP cylinder, compressions begin, for a first compressionstage, at approximately 0 psig and end at approximately 180 psig (shownand labeled as T_(LP)). For the subsequent high-pressure secondcompression stage, three scenarios are shown: (1) a compression from 180psig to a first high pressure of 850 psig (T_(HP(P=850 psi))), (2) acompression from 180 psig to a first high pressure of 3000 psig(T_(HP(P=3000 psi))), and (3) the average of (1) and (2). Forsimplicity, the liquid is presumed not to boil or freeze under any ofthe pressure-and-temperature conditions encountered in the hypotheticalcompressions. The first (lower) solid line of the graph represents thefinal temperature of an LP compression across a range of mass ratiosm_(w)/m_(a); the dotted line represents the final liquid temperatureafter foam compression to 850 psig; the dashed line represents the finalliquid temperature after foam compression to 3,000 psig; and the solidline between the dashed line and the dotted line represents the averageof the 850 psig and 3,000 psig final temperatures.

All four curves in the graph in FIG. 15 are of an approximatelyhyperbolic character, approaching adiabatic conditions as m_(w)/m_(a)goes to zero and approaching zero as m_(w)/m_(a) goes to infinity. Itwill be apparent to persons reasonably familiar with the principles ofthermodynamics, liquids, and mixed-phase systems that low m_(w)/m_(a)(approaching zero) is undesirable because of the temperature extremesthat will be encountered. High temperatures may lead to boiling ofliquid (e.g., when the liquid is separated from the foam and itspressure is reduced), to breakdown of surfactant compounds, or to otherundesirable effects. Similarly, large m_(w)/m_(a) (approaching infinity)requires the pumping of larger fractions of liquid in which no potentialenergy of pressure is stored; further, as m_(w)/m_(a) increases, a pointwill be reached where a “foam” is no longer tenable, but rather a massof liquid is produced in which bubbles of gas are present. Among otherdisadvantages of excessively high m_(w)/m_(a), pistons would be capableof effecting only slight compression of such a mixture. Efficientoperation of a compressed-gas energy storage system is generally notfeasible where the working fluid (e.g., two-phase mixture) is notsignificantly compressible. Therefore, the graph in FIG. 15 supports theconclusion that foams having moderate mass ratios m_(w)/m_(a), e.g., inthe vicinity of m_(w)/m_(a)=2, are likely to be the most efficient whenutilized in compressed-gas energy storage system. Such mass ratiosinclude, for example, mass ratios of 1 to 4, and, more preferably, 1.5to 3.

Employment of two fluid phases (e.g., liquid and gas in a foam) in acompressed-gas energy storage system may entail storage of liquid aswell as of compressed gas, either commingled as foam or separated intoliquid, foam, and gas fractions, although only the compressed gas storessignificant pressure potential energy. Storage of liquid may constitutean additional or parasitic cost for the energy storage system; ifexcessive heat-exchange liquid is stored, the cost-effectiveness of theenergy storage system may be reduced. For storage of large quantities ofcompressed gas, storage cost may even dominate total system cost, and insuch a case, the cost of storing large quantities of liquid may beprohibitive. The graph in FIG. 16 shows additional liquid volume as afraction of gas storage volume (i.e., additional storage volume for atwo-phase system where the liquid is stored in the pressure storagereservoir with the gas relative to storage reservoir volume for gas-onlyin the storage reservoir) as a function of foam mass ratio m_(w)/m_(a)for a compressed gas energy storage system with a maximum pressure of3,000 psig. For mass ratio of zero, there is zero liquid storage. Formass ratio of 5, approximately 1.2 times more liquid volume than gasvolume must be stored. For a mass ratio of approximately 2, a volume ofliquid must be stored that is about half as large as the amount of gasthat must be stored. FIG. 16, like FIG. 15, supports the conclusion thatmass ratios in the vicinity of 2 are likely to support the operation ofan efficient, cost-effective compressed-gas energy storage system.

FIG. 17 is a graph of experimental data comparing the energeticperformance of aqueous foams and droplet sprays in maintainingsubstantially isothermal gas cycling during rapid gas expansions betweenapproximately 3,000 psig and approximately 250 psig. Data are shown forisothermal gas expansions occurring in a high-pressure test stand. Eachsymbol on the graph represents a single isothermal expansion. Heatexchange between the liquid and air is achieved by four methods in theseexperiments: (1) water droplet spray in the gas during compression(filled circles), (2) water droplet spray in the gas prior to expansion(filled triangles), (3) aqueous foam spray in the gas during expansion(open circles), and (4) aqueous foam spray in the gas prior to expansion(open triangles), also termed “foam pre-spray.”

The vertical axis of the graph in FIG. 17 is isothermal efficiency,i.e., work performed by the expanding gas divided by the work expectedby an ideal isothermal expansion. The horizontal axis of the graph inFIG. 17 is relative spray work, i.e., the work required to produce thespray of droplets or foam (e.g., by forcing liquid through a spray head)divided by the total work performed by the gas during the expansion. Forexample, in a given expansion experiment, if 300 kJ of work areperformed by the isothermally expanding gas, and 3 kJ of work arerequired to produce the foam generated during that expansion, then therelative spray work for that experiment is 0.01 (3 kJ divided by 300kJ). Lower relative spray work is desirable because it increases overallsystem efficiency; spray work is in general a parasitic load for anisothermal energy storage and recovery system. Spray pumping work isrelated to sprayed volume multiplied by pressure drop and is the workrequired to force the fluid through, e.g., pipes and nozzles to generatea high-quality spray or aqueous foam that promotes rapid heat transferbetween the sprayed liquid and the expanding or compressing gas bymaximizing surface area and proximity between the liquid and gas.

A third experimental variable in the graph in FIG. 17 is indicated forfoam pre-spray experiments (open triangles) by associating numbers withplotted experimental points. The number by each pre-spray pointspecifies the foam mass ratio for that experiment. Herein, the foam massratio is defined as the ratio of liquid mass to gaseous mass in a givenvolume of aqueous foam. For example, if a cubic meter of a given foamcontains 2 kg of liquid and 1 kg of gas, then the mass ratio of thatfoam is 2.0 (2 kg divided by 1 kg). Mass ratios could be indicated forall points in the graph, but for simplicity are only shown for foampre-spray.

The graph in FIG. 17 supports several statements about the employment offoams for heat transfer in isothermal compressed-gas energy storage andgeneration systems. First, higher isothermal efficiencies (e.g., byapproximately 2 to 5 isothermal efficiency percentage points) areachievable using foam pre-spray than for water spray techniques for asimilar set of experimental conditions. (This statement is alsosupported by the graph in FIG. 15.) Second, the majority of foampre-spray experiments have low relative spray work as well as highisothermal efficiency: note the cluster of foam pre-spray experimentalpoints clustered in the vicinity of relative spray work 0.02 andisothermal efficiencies clustered between 0.92 and 0.95. Third,relatively high isothermal efficiencies (approximately 0.94) areachieved by foam pre-spray, in most cases, by relatively low mass ratios(1.8 to 5.5); again, note the cluster in the vicinity of relative spraywork 0.2, isothermal efficiency 0.92 to 0.95.

A foam contains a large liquid-gas surface contact area, facilitatingheat transfer between the two phases (liquid and gas). Use of foam forheat transfer during isothermal gas expansion or compression offers anumber of advantages over non-foam-based techniques such as dropletsprays. These advantages include the following: (1) For a givenliquid-gas surface contact area (and corresponding heat-transfer rate),a foam may typically be generated using significantly less energy than aspray. (2) Anti-corrosive and/or other agents that may be advantageousto add to a heat-exchange liquid may have intrinsic surfactant (foaming)properties. Thus, multiple advantages, including foaming for heattransfer, may be achieved using a heat-exchange liquid containing only afew additives (or merely one). (3) Droplets tend to settle (rain out) ofa gas rapidly, whereas foams may be relatively persistent, depending onthe properties of the surfactants or other substances responsible forfoaming behavior. Therefore, unlike droplets, foams may be injected intoa gas either while the gas is undergoing expansion or compression withina cylinder chamber or prior to, and/or concurrently with, the transferof the gas into the chamber. Foam generation may thus be locatedexternally to the cylinder, as compared to, for example, placement ofspray heads within the cylinder for generating a droplet spray. Locationof foam generation outside the cylinder has several advantages,including increasing cylinder interior volume and relaxing sizeconstraints on the foam generation mechanism. Locating foam generationoutside the cylinder also enables continuous or episodic foamgeneration, not necessarily synchronized with the operation of thecylinder, whereas foam or spray generation inside the cylinder tends tobe synchronized with the operation of the cylinder. A quantity offoaming liquid may be added to a quantity of gas either during or priorto admission of the gas into a cylinder chamber, substantially fillingthe cylinder chamber with foam. As the gas is expanded or compressed inthe cylinder chamber, the foam is expanded or compressedcorrespondingly, continuing to substantially fill the cylinder chamberthroughout the expansion or compression. Herein, we assume that foamspersistent relative to cylinder stroke time are employed, i.e., foamsthat do not significantly drain over the time-scale on which expansionsand compressions take place in a given system. Foam persistencethroughout expansion or compression facilitates isothermality byenabling heat transfer between the gas and liquid phases to occurthroughout expansion or compression. (4) In the experiments whoseresults are depicted in FIG. 17, only foam experiments achievesimultaneously high isothermal efficiency, low relative spray work, andlow mass ratio: the spray droplet experiments with highest isothermalefficiency (approximately 0.935) have mass ratio above 10 (not shown ongraph) and relative spray work between approximately 0.035-0.095,whereas many foam pre-spray experiments have comparable or higherisothermal efficiencies with relative spray work less than 0.035 andmass ratios of 3.6-5.5. In general, foam pre-spray achieves higherisothermal efficiency and lower relative spray work with lower massratio than do other methods examined in the series of experimentsgraphed in FIG. 17. Lower mass ratio is advantageous because for a givenisothermal efficiency and given start pressure (in expansions) or endpressure (in compressions), in a cylinder of a given volume, a lowermass ratio allows more gas to be compressed or expanded in a singlecycle than does a higher mass ratio, as there is less incompressibleliquid and more gas in the cylinder chamber. Processing more gas percylinder cycle raises overall system power density. An additionaladvantage of lower mass ratio arises as follows: during the injection offluid into a cylinder chamber or during the expulsion of fluid from acylinder chamber, pressure drops occur through valves, with attendantsystem inefficiency. For a given flow rate through a valve, pressuredrop is approximately proportional to the mass density of the fluidpassing through the valve. The average mass density of a foam is lowerfor a foam with lower mass ratio. Thus, throttling losses during thepassage of foam into and out of a cylinder are lower for a foam withlower mass ratio.

Mass ratio remains approximately constant within a closed cylinderduring expansion or compression of a foam. Bubbles in a foam tend togrow during expansion and shrink during compression, but the masses ofthe liquid and gas components generally remain fixed, apart from effectsarising from the dissolving or coming out of solution of gas andvapor-liquid phase changes of the liquid component.

FIG. 18 is a schematic drawing of a system 1800 that may be part of alarger system for energy storage and generation not otherwise depicted.System 1800 has two cylinders 1802 and 1804 and apparatuses 1806, 1808,1810 for the generation and separation of foams 1812, 1814, 1816 havingthree different expansion ratios. Herein, the “expansion ratio” of afoam is the total volume of a given quantity of the foam divided by thevolume of the liquid component of that volume of foam. For example, if 1cubic meter of a foam contains 0.1 cubic meter of liquid, the expansionratio of the foam is 10.0 (1 cubic meter divided by 0.1 cubic meter).Unlike mass ratio, expansion ratio does not tend to remain constant as afoam is expanded or compressed. Rather, expansion ratio tends todecrease as a foam is compressed and increase as it is expanded.

Each foam-generation apparatus 1806, 1808, 1810 features a foam vessel(1818, 1820, and 1822, respectively) and a recirculation pump (1824,1826, and 1828, respectively). Cylinder 1802 operates in a range ofrelatively high pressures (e.g., between approximately 300 psig andapproximately 3,000 psig), and cylinder 1804 operates in a range ofrelatively low pressures (e.g., between approximately 300 psig andapproximately 0 psig). Each foam vessel 1818, 1820, 1822 may include orconsist essentially of a separate pressure vessel (as depicted in FIG.18), piping connected to a cylinder (or a potion thereof), and/or amanifold connected to a cylinder (or a portion thereof).

When system 1800 is operated as an expander, gas from storage (notshown) may be admitted to high-pressure foam vessel 1818 at highpressure. There the gas is combined with heat-exchange liquid to form anaqueous foam (or enhance an already present foam) having a desired massratio. Foam may accumulate in high-pressure foam vessel 1818 prior totransfer to cylinder 1802, be passed to high-pressure cylinder 1802 asit is generated, or both. A mechanism for combining gas withheat-exchange liquid to form an aqueous foam is not depicted in FIG. 18;illustrative mechanisms will be depicted in subsequent figures. Liquidaccumulating in high-pressure foam vessel 1818 due to foam breakdown maybe recirculated into vessel 1818 by the pump 1824. In other embodiments,pump 1824 may be reversed and air or less dense foam from nearer the topof vessel 1818 may be pumped into the bottom of vessel 1818 toregenerate foam (e.g., a sparging process). When system 1800 is operatedas an expander, foam at high pressure from high-pressure vessel 1818 isadmitted to the upper chamber 1830 of cylinder 1802. The foam expands inthe chamber 1830, retaining a constant mass ratio but increasing itsexpansion ratio (e.g., by a factor between approximately 5 andapproximately 15). After expansion of the gas in chamber 1830 to amid-pressure (e.g., approximately 300 psig), the foam is pushed fromchamber 1830 by a return stroke of the piston 1832. The foam exitingchamber 1830 passes into foam vessel 1820. In foam vessel 1820, the foammay be reconstituted by an appropriate mechanism such as one includingrecirculation pump 1826. The foam may accumulate in mid-pressure vessel1820 prior to transfer to cylinder 1804, be passed to cylinder 1804 asit is generated/maintained, or both. The mid-pressure foam vessel 1820contains and generates foam at the mid-pressure of system 1800 (e.g.,approximately 300 psig).

Foam from mid-pressure foam vessel 1820 is admitted to the upper chamber1834 of low-pressure cylinder 1804. The foam expands in the chamber1834, retaining a constant mass ratio during expansion but increasingits expansion ratio (e.g., by a factor of approximately 10 toapproximately 15). After expansion of the gas in chamber 1834 to lowpressure (e.g., approximately 5 psig), the foam is pushed from chamber1834 by a return stroke of the piston 1836. The foam exiting chamber1830 passes into low-pressure foam vessel 1822. In low-pressure foamvessel 1822, the foam is separated into its liquid and gaseouscomponents so that low-pressure gas may be exhausted through vent 1838substantially without loss of heat-exchange liquid from the system 1800.

When system 1800 is operated as a compressor, gas from the environmentmay be admitted to low-pressure foam vessel 1822 at low pressure (e.g.,atmospheric pressure). There the gas is combined with heat-exchangeliquid to form an aqueous foam having a desired mass ratio. Foam mayaccumulate in the low-pressure foam vessel 1822 prior to transfer tocylinder 1804, be passed to low-pressure cylinder 1804 as it isgenerated, or both. Liquid accumulating in low-pressure foam vessel 1822due to foam breakdown may be recirculated into vessel 1822 by the pump1828. When system 1800 is operated as a compressor, foam at low pressurefrom vessel 1822 is admitted to the upper chamber 1834 of cylinder 1804.The foam is compressed in the chamber 1834, retaining a constant massratio but decreasing its expansion ratio. After compression of the gasin chamber 1834 to a mid-pressure (e.g., approximately 300 psig), thefoam is exhausted from chamber 1834. The foam exiting chamber 1834passes into mid-pressure foam vessel 1820. In foam vessel 1820, the foammay be reconstituted by an appropriate mechanism, e.g., one includingrecirculation pump 1826. The foam may accumulate in mid-pressure vessel1820 prior to transfer to cylinder 1802, be passed to cylinder 1802 asit is generated/maintained, or both.

Foam from mid-pressure foam vessel 1820 is admitted to the upper chamber1830 of high-pressure cylinder 1802. The foam is compressed in thechamber 1830, retaining a constant mass ratio during compression butdecreasing its expansion ratio. During or after compression of the gasin chamber 1830 to high pressure (e.g., approximately 3,000 psig), thefoam exits chamber 1830 and passes into high-pressure storage (not shownin FIG. 18) via high-pressure foam vessel 1818. In high-pressure foamvessel 1818, the foam may be separated into its liquid and gaseouscomponents so that high-pressure gas may be transferred to high-pressurestorage substantially without loss of heat-exchange liquid from thesystem 1800. Alternatively or in conjunction, foam may be passed tohigh-pressure storage from vessel 1818 and there stored as an aqueousfoam, separated into its liquid and gas components, or under a partialsuch separation.

The cylinders 1802, 1804 and the foam-generation apparatuses 1806, 1808,1810 may circulate fluid through heat-exchange subsystems, not depictedin FIG. 18, and/or may communicate with a single or multiple thermalwells, not depicted in FIG. 18.

FIG. 19 is a schematic drawing of an illustrative system 1900 thatincludes an apparatus for the generation of foam at low pressure (e.g.,approximately atmospheric pressure) having a high expansion ratio (e.g.,400:1) corresponding to a moderate liquid-to-air mass ratio (e.g., 2:1).System 1900 includes three two-cylinder subsystems (1902, 1904, 1906),depicted in cross-section as viewed from above in a vertically orientedcylinder arrangement, for the isothermal expansion and compression ofgas. The depiction in the illustrative system 1900 of three two-cylindersubsystems is illustrative: other numbers of subsystems, where eachsubsystem includes one, three, or more cylinders, are also contemplatedand within the scope of the invention. Each of the two-cylinder systems1902, 1904, and 1906 includes or consists essentially of a high-pressurecylinder (1908, 1910, and 1912, respectively) and a low-pressurecylinder (1914, 1916, and 1918, respectively). The apparatus for thegeneration of foam may include or consist essentially of a spray chamber1920, a screen 1922, a manifold 1924 that conducts foam (typicallyrepresented in FIG. 19 and elsewhere herein by stippling) to thelow-pressure cylinders 1914, 1916, and 1918, a fan 1926, and an optionalvent and ball valve 1928 whose function shall be described below. Duringthe generation of foam in the apparatus, air at low (e.g., approximatelyatmospheric) pressure is admitted to the spray chamber 1920 through aninlet 1930. The air is accelerated toward the screen 1922 by the fan1926 (or other suitable mechanism). Fluid from a reservoir 1932, foamvessel, or other source is pumped by a pump 1934 to one or more sprayheads 1936 (or other suitable dispersal mechanisms), which are placed inthe flow of gas accelerated by the fan 1930. The spray 1938 from thespray heads 1936 is directed toward the screen 1922 (e.g., metal mesh,netting, solid foam material). Passing through the screen 1922, the airand spray 1938 combine to form an aqueous foam 1940. The foam 1940 maybe directed via suitable valves and pipes (not depicted) into chambersof the low-pressure cylinders 1914, 1916, and 1918.

In a start-up mode of operation where the manifold 1924 initiallycontains no foam, gas may be directed out the valve 1928 (rather thaninto the low-pressure cylinders 1914, 1916, and 1918) during generationof foam until the manifold 1924 is substantially or entirely filled withfoam 1940, whereupon the valve 1928 may be closed and the foam 1940 maybe directed into the low-pressure cylinders 1914, 1916, and 1918. Valve1928, in various embodiments, may be connected to a vent (not shown),have connections that allow any liquid intake to return to the fluidreservoir 1932, and/or may be connected back to the inlet 1930.

The generation capacity of the foam generation apparatus (includingspray chamber 1920, screen 1922, and manifold 1924) depicted in FIG. 19may be sized to correspond to an average foam intake flow for thecylinder or cylinders to which the apparatus supplies foam, or to a peakfoam intake flow. Herein, the generation capacity of a foam generator isthe volume of foam that it can produce per unit time (m³/sec). Rapidfoam flow from a reservoir or pre-generated body of foam may entailshear forces that break down the flowing foam, partly or wholly;generating foam at a sufficient rate may mitigate such shear forces.Other foam generators, both those depicted herein and in embodiments notdepicted herein, may also be sized in order to accommodate peak flowrates and mitigate separation of foams due to shear forces.

FIG. 20 is a schematic drawing of an illustrative system 2000 thatfeatures an apparatus for the generation and separation of aqueous foamat low pressure (e.g., approximately atmospheric pressure) having a highexpansion ratio (e.g., 400:1) corresponding to a moderate liquid-to-airmass ratio (e.g., 2:1). System 2000 includes three two-cylindersubsystems (2002, 2004, 2006), depicted in cross-section as viewed fromabove in a vertically oriented cylinder arrangement, for the isothermalexpansion and compression of gas. The depiction in the illustrativesystem 2000 of three two-cylinder subsystems is illustrative: othernumbers of subsystems, where each subsystem includes one, three, or morecylinders, are also contemplated and within the scope of the invention.

Each of the two-cylinder systems 2002, 2004, and 2006 includes ahigh-pressure cylinder (2008, 2010, and 2012, respectively) and alow-pressure cylinder (2014, 2016, and 2018, respectively). Theapparatus for the generation of foam includes three chambers: a spraychamber 2020; a manifold 2022 that conducts foam to the low-pressurecylinders 2014, 2016, and 2018; and a separation chamber 2024. The spraychamber 2020 is divided from the manifold 2022 by a screen 2024 and maycontain a fan 2026, one or more spray heads 2028, and a louver or flap2030 capable of either blocking or allowing the passage of gas into thespray chamber 2020. Louvre 2030 may act as an air check valve,preventing backflow in the opposite direction of the arrows shown onmanifold 2022. The manifold 2022 is separated from the separationchamber 2024 by a louver or flap 2032 capable of either blocking orallowing the passage of gas and/or foam 2034 from the manifold 2022 intothe separation chamber 2024. The separation chamber 2024 contains a foambreakup mechanism 2036 that separates foam 2034 into a gas component anda liquid component 2038. In FIG. 20, the foam breakup mechanism 2036 isa rotating whisk; other methods and mechanisms for the breakup of foam(e.g., other forms of mechanical agitation, screens, filters,ultrasound) are contemplated and within the scope of the invention. Theliquid 2038 within the separation chamber 2024 is conveyed by piping2040 to a reservoir 2042, from whence it may be pumped by a pump 2044through piping 2046 to the spray heads 2028 for recycling into freshfoam 2034. An atmospheric vent or opening 2048 permits ingress oflow-pressure gas into the spray chamber 2020 during generation of foam2034 and egress of low-pressure gas from the separation chamber 2024during the breakup of foam 2034. During ingress of gas into the spraychamber 2020, an optional cleaning filter 2050 prevents the admissioninto the spray chamber 2020 of particulates and/or other contaminants inthe atmospheric air. During egress of gas from the separation chamber2024, an optional coalescing filter 2052 removes remaining liquid fromfoam, water droplets, and vapor, assuring that nearly no liquid will bepassed to the vent 2048. In various other embodiments, separate ventsmay be provided for ingress of gas into and egress of gas out of thesystem 2000. Also in various other embodiments, the filters 2050, 2052may be located outside the apparatus depicted in FIG. 20 (e.g., in pipesleading to the separate vents provided in various other embodiments).

During operation of system 2000 as a compressor (e.g., to store energyas the pressure potential energy of compressed air), air is admittedthrough vent 2048, passes through a filter 2050, and is accelerated byfan 2026 toward the spray heads 2028 and the screen 2024. Liquid ispumped through the spray heads 2028. (Optionally, fan 2026 may beomitted and air flow may be generated via cylinder piston motion.) Spray2054 mingled with air strikes the screen 2024. A foam 2034 having arelatively high expansion ratio is generated by the passage of mingledair and liquid through the screen 2024. The manifold 2022 conducts thefoam 2034 to the low-pressure cylinders 2014, 2016, and 2018, into whichthe foam 2034 is admitted by appropriate valves (not depicted in FIG.20). The foam 2034 inside the low-pressure cylinders 2014, 2016, and2018 is then compressed to a mid-pressure (e.g., approximately 300psig), after which the foam is transferred to the high-pressurecylinders 2008, 2010, and 2012 and possibly to, or through, otherapparatus not depicted in FIG. 20. Additionally, the amount of foam flowgenerated by fan 2026, spray 2054, and screen 2024 may exceed therequired flow rate of the cylinders 2014, 2016, and 2018 (e.g., bysizing the flow rate to the peak required intake flow of the cylinders)such that excess foam may be generated. This excess foam may be recycledby running through louver 2032, foam breakdown mechanism 2036, andseparation chamber 2024.

During operation of system 2000 as an expander (e.g., to generate energyfrom the pressure potential energy of compressed air), louver 2030 willtypically be closed to prevent backflow through the foam generationequipment 2024, 2028, 2026. After expansion of air in the cylinder pairs2002, 2004, and 2006, foam 2034 at low pressure (e.g., approximately 5psig for an instant and then approximately atmospheric thereafter) exitsthe low-pressure cylinders 2014, 2016, and 2018, passes through themanifold 2022, and enters the separation chamber 2024. In the separationchamber 2024, the low-pressure foam 2034 encounters the foam breakdownmechanism 2036 and is separated into its gas and liquid 2038 components.This separation may not be complete, but at minimum the foam expansionratio will be drastically reduced (e.g., from a 400:1 expansion ratiofoam to a 2:1 expansion ratio foam and air). The liquid 2038 (or lowexpansion-ratio foam) is conveyed to the reservoir 2042 and the gascomponent passes through coalescing filter 2052 and is vented throughvent 2048.

FIG. 21 is a schematic drawing of an illustrative system 2100 featuringan apparatus for the generation of foam at high pressure (e.g., 750 to3,000 psig) having a low expansion ratio (e.g., 8:1 to 2:1)corresponding to a moderate liquid-to-air mass ratio (e.g., 2:1). System2100 includes three two-cylinder subsystems (2102, 2104, 2106), depictedin cross-section as viewed from above in a vertically oriented cylinderarrangement, for the isothermal expansion and compression of gas. Thedepiction in the illustrative system 2100 of three two-cylindersubsystems is illustrative: other numbers of subsystems, where eachsubsystem includes one, three, or more cylinders, are also contemplatedand within the scope of the invention. Each of the two-cylinder systems2102, 2104, and 2106 includes a high-pressure cylinder (2108, 2110, and2112, respectively) and a low-pressure cylinder (2114, 2116, and 2118,respectively). The apparatus for the generation of foam includes orconsists essentially of a spray chamber 2120, an optional vent and ballvalve 2122, and a manifold 2124 that conducts aqueous foam 2126 to thehigh-pressure cylinders 2108, 2110, and 2112. A pump 2128 pumps liquid(or optionally air or liquid and air) from a reservoir or other source2130 to one or more spray heads or other suitable dispersal mechanisms(not depicted) in the spray chamber 2120. Air at high pressure isconducted to the spray chamber 2120 by piping 2132. The passage ofhigh-pressure air through the spray chamber mingles the air with thespray 2134, forming foam 2126. Foam generation at high pressure and lowexpansion ratio is robust and the foam may be generated with or without(i) the use of a screen (such as screen 1224 shown in FIG. 12) and/or(ii) the forced flow of air (e.g., foam may be generated in the absenceof cylinder 2108, 2110, 2112 piston movement and/or a fan). Spray 2134may be all liquid, all air, or a mixture of liquid and air and may besprayed horizontally, vertically upward, vertically downward, oraccording to other arrangements within the spray chamber 2120. In otherembodiments, the high-pressure and low expansion-ratio foam may begenerated by mechanical agitation of the liquid and air, such as throughthe use of a rotating impeller embedded in spray chamber 2120. The foam2126 may be directed via suitable valves and pipes (not depicted) intochambers of the high-pressure cylinders 2108, 2110, and 2112. Reservoir2130 may be the same apparatus as the source for high-pressure air (atpiping 2132), perhaps separated only by location of the piping (e.g.,2132 is connected to the top of a storage reservoir and 2130 is at thebottom of the reservoir such that mostly high-pressure air is directedthrough 2132 and mostly high-pressure liquid is directed through pump2128). The fluid flowing through 2132 may be mostly foam and chamber2120 may act only to refresh, homogenize, change the expansion ratio of,or otherwise refine the aqueous foam.

In a start-up mode of operation where the manifold 2124 initiallycontains no foam, gas may be directed out the valve 2122 (rather thaninto the high-pressure cylinders 2108, 2110, and 2112) during generationof foam until the manifold 2124 is substantially or entirely filled withfoam 2126, whereupon the valve 2122 may be closed and the foam 2126 maybe directed into the high-pressure cylinders 2108, 2110, and 2112. Thehigh-pressure gas or foam directed out of the valve 2122 may berecirculated back into storage reservoir 2130, into pipe 2132, spraychamber 2120, or otherwise recycled. A pump (not shown) may be used todraw fluid from pipe 2132 through valve 2122 and then return the fluidto reservoir 2130, pipe 2132, or spray chamber 2120 in a recycling loop.

FIG. 22 is a schematic drawing of an illustrative system 2200 featuringan apparatus for the generation of foam at mid pressure (e.g., 200 to300 psig) having a medium expansion ratio (e.g., 36:1 to 28:1)corresponding to a moderate liquid-to-air mass ratio (e.g., 2:1). System2200 includes three two-cylinder subsystems (2202, 2204, 2206), depictedin cross-section as viewed from above in a vertically oriented cylinderarrangement, for the isothermal expansion and compression of gas. Thedepiction in the illustrative system 2200 of three two-cylindersubsystems is illustrative: other numbers of subsystems, where eachsubsystem includes one, three, or more cylinders, are also contemplatedand within the scope of the invention. Each of the two-cylinder systems2202, 2204, and 2206 includes a high-pressure cylinder (2208, 2210, and2212, respectively) and a low-pressure cylinder (2214, 2216, and 2218,respectively). The apparatus for the generation of foam includes orconsists essentially of a combined spray chamber and manifold 2220 inwhich foam 2222 is generated or regenerated and which conducts foam 2222from the high-pressure cylinders 2208, 2210, and 2212 to thelow-pressure cylinders 2214, 2216, 2218 (during expansion) or from thelow-pressure cylinders 2214, 2216, 2218 to the high-pressure cylinders2208, 2210, and 2212 (during compression).

During expansion or compression, foam having an intermediate expansionratio at intermediate pressure enters the chamber/manifold 2220. A pump2224 draws fluid (e.g., air, foam, or liquid separated from foam inchamber/manifold 2220) and injects the fluid back into chamber/manifold2220 through nozzles or heads 2226 (or other suitable dispersalmechanisms). The injected fluid 2228 takes up residence in thechamber/manifold 2220 in the form of a sufficiently stable aqueous foam2222 that may be directed via suitable valves and pipes (not depicted)into chambers of either the high-pressure cylinders 2208, 2210, and 2212or the low-pressure cylinders 2214, 2216, 2218. Additional components,not shown, may be used to aid in the generation of foam, such asscreens, meshes, or solid foams.

Various embodiments employ efficient pumping schemes for the circulationof foam or of heat-exchange liquid that may be foamed. FIG. 23 depictsan illustrative system 2300 that compresses or expands gas. The system2300 employs a pneumatic cylinder 2304 that contains a slidably disposedpiston 2306 that divides the interior of the cylinder 2304 into a distalchamber 2308 and a proximal chamber 2310. A port or ports (not shown)with associated pipes 2312 and a bidirectional valve 2314 enables gasfrom a high-pressure storage reservoir 2316 to be exchanged with chamber2308 as desired. The high-pressure storage reservoir may act as aseparator, in which the liquid component of a foam may be separated fromthe gas component of the foam. In an alternative embodiment, a distinctseparator (not shown) component may be employed to separate liquid andgas, and may contain elements to facilitate separation and foambreakdown including baffles, mechanical shear elements, meshes,ultrasonic shear elements, and/or other such elements. A port or ports(not shown) in the end-cap of the air chamber of the cylinder 2304, withassociated pipe 2318 and a bidirectional valve 2320, enables fluid fromthe chamber 2308 to be admitted from or exhausted to the ambientatmosphere as desired through a vent 2322. In alternate embodiments, notshown, vent 2322 is replaced by one or more additional pneumaticcylinders. A port or ports, not shown, enables the interior of the lowerchamber 2310 of the pneumatic cylinder 2304 to communicate freely at alltimes with the ambient atmosphere. In alternate embodiments, cylinder2304 is double-acting and chamber 2310 is, like chamber 2308, equippedto exchange, in various states of operation, fluids with either high- orlow-pressure reservoirs and/or additional cylinders.

The distal end (i.e., upper end, for the illustrative verticalorientation of cylinder 2304 in FIG. 23) of a rod 2324 is coupled to thepiston 2306. The proximal (lower) end of rod 2324 may be connected tosome mechanism, such as one or more hydraulic cylinders or a crankshaft(not shown), for interconverting linear mechanical power and rotarymechanical power.

In an energy-recovery or expansion mode of operation, storage reservoir2316 is filled with high-pressure fluid 2326 and a quantity ofheat-transfer fluid 2328. The fluid 2326 may consist essentially orprimarily either of gas or of foam. The heat-exchange fluid 2328 may bea liquid that tends to foam when sprayed or acted upon in some othermanner. The accumulation of heat-exchange fluid 2328 depicted at thebottom of vessel 2316 may consist essentially or primarily either ofliquid or of foam. A quantity of gas may begin to be introduced viavalve 2314 and pipe 2312 into the upper chamber 2308 of cylinder 2304when piston 2306 is near or at the top of its stroke (i.e., “top deadcenter” of cylinder 2304). The piston 2306 and its rod 2324 will then bemoving downward (the cylinder 2304 may be oriented arbitrarily but isshown vertically oriented in this illustrative embodiment).Heat-exchange fluid 2328 may be injected into chamber 2308 via one ormore spray heads 2330. The spray-head 2330 depicted in FIG. 23 isillustrative only; other devices (e.g., one or more nozzles or arotating blade) may be used to introduce heat-exchange fluid into theair chamber 2308. In the illustrative embodiment of FIG. 23, foam can begenerated or regenerated within cylinder 2304 by injection of fluidthrough a mechanism (e.g., the spray head 2330); in various otherembodiments, foam is generated externally to cylinder 2304 (by amechanism not depicted in FIG. 23). Heat-exchange fluid (liquid or foam)may partially or entirely fill the chamber 2308. An accumulation offluid 2332 (liquid or foam) may occur on the upper surface of the piston2306.

The system 2300 is instrumented with pressure, piston position, and/ortemperature sensors (not shown) and controlled via a control system (notshown). The system 2300 also features a pump cylinder 2334 for supply ofpressurized heat-exchange fluid to the spray head 2330. The pumpcylinder 2334 contains a slidably disposed piston 2336 that divides theinterior of the cylinder 2334 into an upper chamber 2338 and a lowerchamber 2340. Heat-exchange fluid may partially or entirely fill theupper chamber 2338 of the pump cylinder 2334. A port or ports (notshown), with associated pipe 2342 and a bidirectional valve 2344,enables fluid 2346 from a low-pressure reservoir 2348 to be exchangedwith chamber 2338 as desired. The reservoir may act as a foam reservoirand/or as separator that divides the liquid component of a foam from thegas component of the foam. A port or ports, not shown, enables theinterior of the lower chamber 2340 of the pump cylinder 2334 tocommunicate freely at all times with the ambient atmosphere. The piston2336 is coupled to a rod 2350. The rod 2324 of the pneumatic cylinder2304 and the rod 2350 of the pump cylinder 2334 may be joined to asingle mechanical device (not shown), e.g. a crankshaft, which maintainsthem in a fixed phase relationship (e.g., rod 2350 may reach its maximumupward displacement whenever rod 2324 reaches its maximum downwarddisplacement). The pump cylinder 2334 may be oriented arbitrarily but isshown vertically oriented in this illustrative embodiment.

Heat-exchange fluid 2346 in the low-pressure reservoir 2348 is mixableand/or exchangeable with heat-exchange fluid 2328 in the high-pressurestore 2316, the accumulation of fluid 2332 in the pneumatic cylinder2304, and the fluid within the upper chamber 2338 of the pump cylinder2334. That is, all these bodies of fluid are labeled separately forclarity in FIG. 23, but in the course of operation of the system 2300may be mingled and exchanged with each other as well as with anyheat-exchange fluid present in pipes, valves, and other components ofthe system 2300. Preferably, the accumulations 2328, 2346 ofheat-exchange fluid in the two reservoirs 2316, 2348 in FIG. 23 includeor consist essentially of un-foamed (but foamable) heat-exchange liquid.Two methods of operation of the system 2300, namely the “open-loopmethod” and the “closed-loop method,” are described hereinbelow. The twomethods described herein are illustrative, not exhaustive, of themethods according to which system 2300 may be operated. Also, therelative timing or phasing of various steps in these two methods ofoperation as described herein are illustrative: other patterns ofrelative timing or phasing are contemplated and within the scope of theinvention.

Each of these two methods of operation of system 2300 described herein(i.e., closed-loop method and open-loop method) has a compression mode,in which gas is compressed in order to store energy, and an expansionmode, in which gas is expanded to release energy.

Open-Loop Method of Operation: Compression Mode

In an initial state of one mode of operation of the system 2300, hereintermed the “open-loop compression” method of operation, piston 2306 isat top dead center of pneumatic cylinder 2304 and piston 2336 is topdead center of pump cylinder 2334. Valves 2314, 2346, and 2352 areclosed, and valves 2320 and 2344 are open. Piston 2306 and piston 2336move downward, admitting a quantity of low-pressure gas into chamber2308 of the pneumatic cylinder 2304 and a quantity of heat-exchangefluid 2346 (preferably liquid) from low-pressure reservoir 2348 intochamber 2338 of the pump cylinder 2334. Downward motion of the piston2306 to its nethermost limit of motion (i.e., “bottom dead center”position), with filling of chamber 2308 with gas, constitutes an “intakestroke” of cylinder 2304. Downward motion of the piston 2336 to itsnethermost limit of motion (i.e., “bottom dead center” position), withfilling of chamber 2338 with heat-exchange fluid, constitutes an “intakestroke” of the pump cylinder 2334.

Valves 2320 and 2344 may then be closed and valve 2346 opened, and thepistons 2306 and 2336 may begin upward strokes in their respectivecylinders. The upward motion of piston 2306 tends to compress the fluidwithin chamber 2308 of the pneumatic cylinder 2304, and the upwardmotion of piston 2336 tends to expel fluid from chamber 2338 of the pumpcylinder 2334. Fluid expelled from chamber 2338 of the pump cylinder2334 passes through valve 2346 and an optional heat exchanger 2354 thatmay alter the temperature of the fluid. The fluid then passes intochamber 2308 of cylinder 2304 through the spray head 2330, forming aspray 2356. The fluid 2356 either enters the chamber 2308 as a foam orforms a foam by mingling with the gas within chamber 2308. The fluid2356 may partially or entirely fill chamber 2308 and may form anaccumulation of fluid 2332 atop piston 2306. The accumulation of fluid2332 may include or consist essentially of foam or of liquid separatedfrom foam within chamber 2308.

At a predetermined point in the upward (compression) stroke of piston2306, valve 2314 may be opened, allowing pressurized fluid, possiblyincluding heat-exchange fluid 2332 (e.g., as the liquid component of afoam), to flow through piping 2312 into the high-pressure store 2316.Heat-exchange fluid 2332 expelled from chamber 2308 by piston 2306 mayform or add to the accumulation of fluid 2328 within the high-pressurestore 2316. The accumulation of fluid 2328 may include or consistessentially of heat-exchange liquid separated from foam in reservoir2316.

Upward motion of the piston 2306 to its limit of motion (top deadcenter), with expulsion of pressurized gas and fluid into store 2316,constitutes a “compression stroke” of pneumatic cylinder 2304. Acomplete compression stroke in the open-loop method of operation ofsystem 2300 entails one-way or “open-loop” passage of heat-exchangefluid (preferably liquid) 2346 out of the low-pressure reservoir 2348,through chamber 2338 of the pump cylinder 2334, through the optionalheat exchanger 2354, into chamber 2308 of the pneumatic cylinder 2304,and into the high-pressure store 2316, successively. During one or moresuccessive cycles of system 2300 in open-loop compression mode asdescribed hereinabove, heat-exchange liquid 2328 may accumulate in thehigh-pressure store 2316.

The sequence of operations described above for the compression mode ofthe closed-loop method of operation is illustrative, and may be variedin this and other embodiments. Sequences of operations described forother modes and methods of operation below are also illustrative andmight be varied in other embodiments.

Open-Loop Method of Operation: Expansion Mode

In an initial state of another mode of operation of the system 2300,herein termed the “open-loop expansion” mode of operation, piston 2306is at top dead center of pneumatic cylinder 2304 and piston 2336 is atbottom dead center of pump cylinder 2334. Chamber 2338 of pump cylinder2334 is filled with heat-exchange fluid (preferably liquid). Valves2320, 2344, and 2352 are closed and valves 2314 and 2346 are open.Piston 2306 moves downward, admitting a quantity of high-pressure gasinto chamber 2308 of the pneumatic cylinder 2304. Simultaneously, piston2336 of the pump cylinder 2334 moves upward. Heat-exchange fluid fromchamber 2338 passes through valve 2346, optional heat exchanger 2354,and spray head 2330 to enter chamber 2308 of the pneumatic cylinder. Atsome subsequent, predetermined point, valve 2314 may be closed whilepiston 2306 continues its downward motion and piston 2336 continues itsupward motion.

The motion of piston 2306 from top dead center to bottom dead center ofpneumatic cylinder 2304 during and after the introduction into chamber2308 of high-pressure gas (or foam) from store 2316 is herein termed an“expansion stroke” of pneumatic cylinder 2304. The motion of piston 2336from bottom dead center to top dead center of pump cylinder 2334 isherein termed a “pumping stroke” of pump cylinder 2334. The expansionstroke of pneumatic cylinder 2304 and the pumping stroke of pumpcylinder 2334, as well as other cylinder strokes of this and otherembodiments described herein, may be of equal duration and may begin andend simultaneously, or they may be of different durations and may notbegin or end simultaneously.

Subsequent to the completion of the expansion stroke and pumping stroke,valves 2314 and 2346 may be closed and valves 2320 and 2352 opened.Piston 2306 of the pneumatic cylinder then moves from bottom dead centerto top dead center while the fluid within chamber 2308 is expelled.Preferably, the expelled fluid includes or consists essentially of foamand enters vessel 2348, where it is separated into its gas and liquidcomponents so that its gas component may be exhausted through vent 2322and its liquid component 2332 may accumulate as liquid 2346 in thelow-pressure reservoir 2348. Upward motion of the piston 2306 frombottom dead center to top dead center with expulsion of low-pressure gasand liquid from chamber 2308 constitutes an “exhaust stroke” of cylinder2304. Concurrently, cylinder 2334 performs an intake stroke, i.e.,piston 2336 moves from top dead center to bottom dead center and chamber2336 fills with heat-exchange fluid (preferably liquid) 2328 from thehigh-pressure store 2316.

An expansion stroke of cylinder 2304 in the open-loop method ofoperation of system 2300 entails one-way or “open-loop” passage ofheat-exchange fluid 2328 out of the high-pressure store 2316, throughchamber 2338 of the pump cylinder 2334, through the optional heatexchanger 2354, into chamber 2308 of the pneumatic cylinder 2304, andinto the low-pressure reservoir 2348, successively. During one or moresuccessive cycles of system 2300 in open-loop expansion mode,heat-exchange fluid 2328 is removed from the high-pressure store 2316and accumulates as liquid 2346 in the low-pressure reservoir 2348. Aperiod of operation of system 2300 in open-loop compression mode willtend to cause an accumulation 2328 of heat-exchange liquid in thehigh-pressure store 2316; a subsequent period of operation of system2300 in open-loop expansion mode will tend to remove the accumulation2328 of heat-exchange liquid from the high-pressure store 2316 andreturn it to the low-pressure reservoir 2348.

Closed-Loop Method of Operation: Compression Mode

In an initial state of another mode of operation of the system 2300,herein termed the “closed-loop compression” method of operation, piston2306 is at top dead center of pneumatic cylinder 2304 and piston 2336 istop dead center of pump cylinder 2334. Valves 2314, 2344, and 2346 areclosed, and valves 2320 and 2352 are open. Piston 2306 and piston 2336move downward, admitting a quantity of low-pressure fluid (gas or foam)into chamber 2308 of the pneumatic cylinder 2304 and a quantity ofheat-exchange fluid (preferably liquid) 2328 from high-pressure store2316 into chamber 2338 of the pump cylinder 2334. Pneumatic cylinder2304 performs an intake stroke and pump cylinder 2334 performs an intakestroke.

Valves 2320 and 2352 may then be closed and valve 2346 opened, and thepistons 2306 and 2336 may begin upward strokes in their respectivecylinders. The upward motion of piston 2306 tends to compress the fluidwithin chamber 2308 of the pneumatic cylinder 2304, and the upwardmotion of piston 2336 tends to expel fluid from chamber 2338 of the pumpcylinder 2334. Fluid expelled from chamber 2338 of the pump cylinder2334 passes through valve 2346 and an optional heat exchanger 2354 thatmay alter the temperature of the fluid. The fluid then passes intochamber 2308 of cylinder 2304 through spray head 2330. The fluid maypartially or entirely fill chamber 2308 with foam. An accumulation 2332of fluid may form on top of piston 2306. At a predetermined point in theupward (compression) stroke of piston 2306, valve 2314 may be opened,allowing pressurized gas and/or foam to flow through piping 2312 intothe high-pressure store 2316. Heat-exchange fluid 2332 expelled fromchamber 2308 by piston 2306 may form an accumulation of fluid 2328within the high-pressure store 2316. The accumulation of fluid 2328 mayinclude or consist essentially of foam or of liquid separated from foamwithin reservoir 2316.

Upward motion of the piston 2306 to its limit of motion (top deadcenter), with expulsion of pressurized fluid into store 2316,constitutes a “compression stroke” of pneumatic cylinder 2304. Acompression stroke in the closed-loop method of operation of system 2300entails cyclic or closed-loop passage of heat-exchange fluid (preferablyliquid) 2328 out of chamber 2308 of the pneumatic cylinder 2304, intothe high-pressure store 2316, into chamber 2338 of the pump cylinder2334, through the optional heat exchanger 2354, and into chamber 2308 ofthe pneumatic cylinder 2304 successively.

Closed-Loop Method of Operation: Expansion Mode

In an initial state of another mode of operation of the system 2300,herein termed the “closed-loop expansion” mode of operation, piston 2306is at top dead center of pneumatic cylinder 2304 and piston 2336 is atbottom dead center of pump cylinder 2334. Chamber 2338 of pump cylinder2334 is filled with heat-exchange fluid. Valves 2320, 2344, and 2352 areclosed and valves 2314 and 2346 are open. Piston 2306 moves downward,admitting a quantity of high-pressure gas (or foam) into chamber 2308 ofthe pneumatic cylinder. Simultaneously, piston 2336 moves upward.Heat-exchange fluid (preferably liquid) from chamber 2338 passes throughvalve 2346, optional heat exchanger 2354, and spray head 2330 to enterchamber 2308 of the pneumatic cylinder. At some subsequent,predetermined point, valve 2314 may be closed while piston 2306continues its downward motion and piston 2336 continues its upwardmotion. Pneumatic cylinder 2304 performs an expansion stroke and pumpcylinder 2334 performs a pumping stroke.

Subsequent to the completion of the expansion stroke of cylinder 2304and the pumping stroke of pump cylinder 2334, valves 2314 and 2346 maybe closed and valves 2320 and 2352 opened. Piston 2306 of the pneumaticcylinder 2304 then moves from bottom dead center to top dead centerwhile the low-pressure fluid within chamber 2308 is expelled throughpipe 2318. Preferably, the expelled fluid includes or consistsessentially of foam and enters vessel 2348, where it is separated intoits gas and liquid components so that its gas component may be exhaustedthrough vent 2322 and its liquid component 2332 may accumulate as liquid2346 in the low-pressure reservoir 2348. Pneumatic cylinder 2304performs an exhaust stroke. Simultaneously, the pump cylinder 2334performs an intake stroke.

An expansion stroke in the closed-loop method of operation of system2300 entails cyclic or “closed-loop” passage of heat-exchange fluid 2332out of chamber 2308 of the pneumatic cylinder 2304, into thelow-pressure reservoir 2348, through chamber 2338 of the pump cylinder2334, through the optional heat exchanger 2354, and into chamber 2308 ofthe pneumatic cylinder 2304 successively.

Various other embodiments employ a pneumatic cylinder that also acts asa pump in order to efficiently circulate heat-exchange fluid (e.g., foamor a foaming liquid) in an energy storage system. FIGS. 24A and 24Bdepict a pneumatic cylinder 2400 that compresses or expands gas andsimultaneously acts as a liquid pump. FIG. 24A depicts one state ofoperation of cylinder 2400; FIG. 24B depicts another state of operationof cylinder 2400.

The cylinder 2400 contains a slidably disposed piston 2406 that dividesthe interior of the cylinder 2400 into a distal (upper) chamber 2408 anda proximal (lower) chamber 2410. A port or ports (not shown) withassociated piping 2412 and bidirectional valves 2414, 2416 enables theupper chamber 2408 to be placed in fluid communication with either (a) ahigh-pressure fluid storage reservoir (not shown, but indicated by theletters “HP”) or (b) a low-pressure fluid reservoir (not shown, butindicated by the letters “LP”). The LP reservoir may contain liquid atlow pressure and its gaseous portion may communicate freely with theambient atmosphere through a vent (not shown). A port or ports (notshown) places the lower chamber 2410 of the first cylinder in continuousfluid communication with gas at low pressure (e.g., the ambientatmosphere). Cylinder 2400 incorporates a tube 2418 that may becylindrical in cross-section and is connected at its upper end to theupper end-cap of the cylinder 2400. The tube 2418 is hollow and may befilled with heat-exchange liquid. The piston 2406 is connected to a rod2422 that contains a center-drilled hollow or cavity 2420, herein termedthe rod cavity 2420, that may be filled with heat-exchange liquid. Thetube 2418 is open at its proximal (lower) end, and is long enough sothat the cavity within the tube 2418 is in constant fluid communicationwith the rod cavity 2420 (e.g., even when piston 2406 is at bottom deadcenter). Gasketing 2424 allows the tube 2418 to telescope within the rod2422 as the rod 2422 and piston 2406 move and prevents fluidcommunication between the upper chamber 2408 and the communicatingcavities of the tube 2418 and rod 2422. When piston 2406 and rod 2422move upward, as depicted in FIG. 24A, the total volume of thecommunicating cavities within the tube 2418 and the rod 2422 decreases,tending to pressurize the fluid within the communicating cavities and toexpel it from the communicating cavities through the tube 2418. Whenpiston 2406 and rod 2422 move downward, as depicted in FIG. 24B, thetotal volume of the communicating cavities within the tube 2418 and therod 2422 will increase, tending to lower the pressure of the fluidwithin the communicating cavities and/or to admit fluid into thecommunicating cavities through the tube 2418. By integrating the pumpinto a rod of a cylinder, higher efficiency may be achieved byeliminating separate or additional crankshaft throws or other mechanicaldrive connections.

FIG. 25 depicts a system 2500 that employs two cylinders of the typedepicted in FIGS. 24A and 24B to compress and/or expand gas. Unlikesystem 2300 in FIG. 23, system 2500 does not employ a discrete orseparate water pump (e.g., pump cylinder 2334 in FIG. 23) in order toefficiently circulate heat-exchange liquid.

The system 2500 employs two cylinders 2402, 2404 (hereinafter termed thefirst cylinder and the second cylinder), both cylinders 2402, 2404 beingsimilar to the cylinder 2400 depicted in FIGS. 24A and 24B. The secondcylinder 2404 contains a slidably disposed piston 2426 that divides theinterior of the second cylinder 2404 into a distal (upper) chamber 2428and a proximal (lower) chamber 2430. A port or ports (not shown) withassociated pipe 2432 and bidirectional valves 2434, 2436 enables theupper chamber 2428 to be placed in fluid communication with either (a) ahigh-pressure fluid storage reservoir (not shown, but indicated by theletters “HP”), preferably the same as that to which the first cylinder2402 may be connected through valve 2414, or (b) a low-pressure fluidreservoir (not shown, but indicated by the letters “LP”), preferably thesame as that to which the first cylinder 2402 may be connected throughvalve 2416. The LP reservoir may contain liquid at low pressure and itsgaseous portion may communicate freely with the ambient atmospherethrough a vent (not shown). A port or ports (not shown) places the lowerchamber 2430 in continuous fluid communication with gas at low pressure(e.g., the ambient atmosphere).

Cylinder 2404 also, like cylinder 2402, incorporates a hollow tube 2438that may be cylindrical in cross-section and is connected at its upperend to the distal end-cap of the cylinder 2404. The interior of the tube2438 may be filled with heat-exchange liquid. The piston 2426 isconnected to a rod 2442 that contains a center-drilled rod cavity 2440that may be filled with heat-exchange liquid. The tube 2438 is open atits lower end and the cavity within the tube 2438 is in fluidcommunication with the rod cavity 2440. Gasketing 2443 allows the tube2438 to telescope within the rod 2442 as the rod 2442 and piston 2426move and prevents fluid communication between the upper chamber 2428 andthe communicating cavities of the tube 2438 and rod 2442. When piston2426 and rod 2442 move upward, the total volume of the communicatingcavities within the tube 2438 and the rod 2442 will decrease, tending topressurize the fluid therein.

The upper end of tube 2418 in the first cylinder 2402 is connected tobidirectional valves 2444, 2446, 2448. Valve 2444 may place the interiorof tube 2418 in fluid communication with a high-pressure storagereservoir (HP); valve 2446 may place the interior of tube 2418 in fluidcommunication with a low-pressure reservoir (LP); and valve 2448 maypermit fluid to flow from the interior of the tube 2418, throughoptional heat exchanger 2450, and thence to a spray head 2452 withinchamber 2428 of the second cylinder 2404. Foaming liquid 2454 passingthrough spray head 2452 enters chamber 2428. The spray heads 2452, 2464depicted in FIG. 25 are illustrative only: other devices (e.g., rotatingblades) may be used to introduce heat-exchange fluid into the airchambers 2408, 2428. In the illustrative embodiment of FIG. 25, foam maybe generated or regenerated within cylinders 2402, 2404 by injection offluid through an appropriate mechanism (e.g., the spray heads 2452,2464); in various other embodiments, foam is generated externally to thecylinders 2402, 2404 (as described elsewhere herein) by mechanisms notdepicted in FIG. 25.

Similarly, the upper end of tube 2438 in cylinder 2404 is connected tobidirectional valves 2456, 2458, 2460. Valve 2456 may place the interiorof tube 2438 in fluid communication with a high-pressure storagereservoir (HP), preferably the same as that with which tube 2418communicates via valve 2444; valve 2458 may place the interior of tube2438 in fluid communication with a low-pressure reservoir (LP),preferably the same as that with which tube 2418 communicates via 2446;and valve 2460 may permit fluid to flow from the interior of the tube2438, through optional heat exchanger 2462, and thence to spray head2464 within chamber 2408 of cylinder 2402. Liquid passing through sprayhead 2464 enters chamber 2408, preferably forming a foam within thechamber 2408.

The valves 2444, 2456 permit fluid communication with that portion ofthe HP store to which heat-exchange liquid may settle (e.g., separatefrom a foam) under the influence of gravity, and therefore tend tocontrol the passage of liquid rather than of gas or foam.

The system 2500 is instrumented with pressure, piston position, and/ortemperature sensors (not shown) and controlled via a control system (notshown). The proximal (lower) ends of the rods 2422, 2442 may beconnected to a mechanism, such as one or more hydraulic cylinders or acommon crankshaft (not shown), for interconverting linear mechanicalpower and rotary mechanical power, as described in the '678 and '842patents.

System 2500 may be operated in such a way that the cavity 2420 withinrod 2422 of the first cylinder 2402 acts as a pump driving heat-exchangefluid into chamber 2428 of second cylinder 2404 during expansion orcompression of gas in chamber 2428, and the cavity 2440 within rod 2442of second cylinder 2404 acts as a pump driving heat-exchange liquid intochamber 2408 of first cylinder 2402 during expansion or compression ofgas in chamber 2408. A discrete or separate pump for circulatingheat-exchange liquid is rendered unnecessary by this method.

Like system 2300 in FIG. 23, system 2500 may be operated according to atleast two methods of operation, namely the “open-loop method” and the“closed-loop method.” These two methods of operation are exemplary, notexhaustive, of the methods according to which system 2500 may beoperated. Each of these two methods of operation of system 2500 (i.e.,closed-loop method and open-loop method) has a compression mode, inwhich gas is compressed in order to store energy, and an expansion mode,in which gas is expanded to release energy.

Open-Loop Method of Operation: Expansion Mode

In one mode of operation of the system 2500, herein termed the“open-loop expansion” method of operation, the second cylinder 2404performs an expansion stroke while the first cylinder 2402 performs anexhaust stroke and sprays foaming heat-exchange liquid into the secondcylinder 2404: the two cylinders may then reverse roles, and mayalternate intake and expansion strokes for as long as expansion of gasby system 2500 is desired.

In an initial state of operation of the open-loop expansion method ofoperation, piston 2406 of the first cylinder 2402 is at bottom deadcenter and piston 2426 of the second cylinder 2404 is at top deadcenter. Valves 2416, 2448, 2458, and 2434 are open and all other valvesare closed. Valve 2416 allows low-pressure air to exit chamber 2408 ofthe first cylinder 2402 while piston 2406 performs an upward (exhaust)stroke; valve 2448 allows heat-exchange liquid to flow from the rodcavity 2420 of the first cylinder 2402, through optional heat exchanger2450, and through the spray head 2452 of the second cylinder 2404,preferably forming a foam 2454 therein; valve 2458 allows heat-exchangefluid from the low-pressure (LP) reservoir to enter the rod cavity 2440of the second cylinder 2404; and valve 2434 allows gas from thehigh-pressure store to enter the upper chamber 2428 of the secondcylinder 2404. In this initial state of operation, a liquid accumulation2466 may be present atop piston 2406 and a liquid accumulation 2468 atoppiston 2426 is slight or absent. Subsequent to this initial state ofoperation, the foam 2454 may enable isothermal expansion of the gaswithin chamber 2428 and may form a fluid accumulation 2468 atop thepiston 2426.

At a predetermined point during the expansion stroke of the secondcylinder 2404, valve 2434 may be closed, preventing the admission ofmore high-pressure gas to the upper chamber 2428. Gas already admittedto the chamber 2428 will continue to expand, and piston 2426 and itsassociated rod 2442 move downward until they reach bottom dead center.Concurrently, piston 2406 and its associated rod 2422 move to top deadcenter, performing an exhaust stroke. Any liquid accumulation 2466 atoppiston 2406 of the first cylinder 2402 will be expelled into the LPreservoir during the latter portion of the exhaust stroke.

By opening valves 2414, 2460, 2436, and 2446 and closing all othervalves, system 2500 may then be placed in a state of operation similarto the initial state of operation of the open-loop expansion method ofoperation described above, except that the roles of the two cylindersare reversed: i.e., first cylinder 2402 is prepared to execute anexpansion stroke and the second cylinder 2404 is prepared to execute anexhaust stroke. Expansion cycles in which the first cylinder 2402expands gas may alternate indefinitely (limited by the capacity of theHP store) with expansion cycles in which the second cylinder 2404expands gas.

While the second cylinder 2404 performs an expansion stroke,heat-exchange fluid at low pressure fills the rod cavity 2440 of thesecond cylinder 2404 through valve 2458. Concurrently, heat-exchangefluid in the rod cavity 2420 of the first cylinder 2402 is pressurizedand expelled through valve 2448. Thus, the first cylinder 2402, duringits exhaust stroke, acts as a pump supplying heat-exchange liquid to thesecond cylinder 2402 as the latter performs an expansion stroke.Similarly, when the second cylinder 2404 performs an exhaust strokewhile the first cylinder 2402 performs a concurrent expansion stroke,the second cylinder 2404 acts as a pump supplying heat-exchange liquidto the first cylinder 2402.

Open-Loop Method of Operation: Compression Mode

In another mode of operation of the system 2500, herein termed the“open-loop compression” method of operation, the two cylinders 2402,2404 perform concurrent compression strokes while injectingheat-exchange fluid into each other's upper chambers 2408, 2428. The twocylinders then perform concurrent gas intake strokes while refillingtheir rod chambers 2420, 2440 with heat-exchange liquid.

In an initial state of operation in open-loop compression mode, pistons2406, 2426 are both at bottom dead center of their respective cylinders2402, 2404, and any liquid accumulations 2466, 2468 atop the pistons2406, 2426 are slight or absent. Valves 2448 and 2460 are open and allother valves are closed. The upper chambers 2408, 2428 of the cylindercontain gas at low pressure. Pistons 2406, 2426 and their associatedrods 2422, 2442 begin to move upward, tending to pressurize the fluid inthe upper chambers 2408, 2428 of the cylinders 2402, 2404. Heat-exchangeliquid expelled from the rod cavities 2420, 2440 passes through thetubes 2418, 2438, valves 2448, 2460, optional heat exchangers 2450,2462, and spray heads 2464, 2452, injecting fluid (preferably as foam,e.g., foam 2454) into the chambers 2408, 2428. This foam may enableisothermal expansion of the gas within chambers 2408, 2428 and may formfluid (foam and/or liquid) accumulations 2466, 2468 atop the pistons2406, 2426. At a predetermined point in the concurrent compressionstrokes of the pistons 2406, 2426, valves 2414, 2434 may be opened,allowing pressurized fluid (gas or foam) to flow into the high-pressure(HP) store (not shown). Heat-exchange fluid 2466, 2468 expelled fromchambers 2408, 2428 by pistons 2406, 2426 may cause an accumulation offluid (e.g., separated liquid) to form within the HP store.

Pistons 2406, 2426 move upward during the concurrent compression strokesexecuted by the two cylinders 2402, 2404 until the pistons 2406, 2426are at top dead center of their respective cylinders 2402, 2404. In asubsequent state of operation, valves 2416, 2446, 2458, and 2436 areopened and all other valves are closed, and the pistons 2406, 2426 andtheir associated rods 2422, 2442 move downward until they reach bottomdead center of their respective cylinders 2402, 2404, filling the upperchambers 2408, 2428 with low-pressure gas and the rod cavities 2420,2440 with low-pressure heat-exchange liquid from the low-pressure (LP)reservoir, thus preparing the system for another concurrent compressionstroke.

A compression stroke in the open-loop method of operation of system 2500entails one-way or “open-loop” passage of heat-exchange fluid out of theLP reservoir, into the rod cavities 2420, 2440 of the cylinders 2402,2404, through the spray heads 2464, 2452 into the upper chambers 2408,2428 of the cylinders 2402, 2404, and thence into the HP store,successively. During one or more successive cycles of system 2500 inopen-loop compression mode, heat-exchange liquid is thus removed fromthe LP reservoir and accumulates in the HP store. A period of operationof system 2500 in open-loop compression mode (e.g., a number of suchcycles) will tend to cause an accumulation of heat-exchange liquid inthe HP store; a subsequent period of operation of system 2500 inopen-loop expansion mode will tend to remove the accumulation ofheat-exchange liquid from the HP store and return it to the LPreservoir.

It will be apparent to any person reasonably well acquainted with theart of hydraulic machinery that system 2500 may also be operatedaccording to a closed-loop method having both expansion and compressionmodes. Such a method of operation will (i) shift accumulatedheat-exchange liquid 2466, 2468 into the HP store during eachcompression and refill the rod cavities 2420, 2440 of the cylinders2402, 2404 from the HP store rather than from the LP reservoir, and/or(ii) shift accumulated heat-exchange liquid 2466, 2468 into the LPreservoir during each expansion and refill the rod cavities 2420, 2440of the cylinders 2402, 2404 from the LP reservoir rather than from theHP store.

The use of cylinders 2402, 2404 for both gas expansion/compression andheat-exchange fluid pumping may increase system efficiency andreliability as compared to a system employing a discrete or separatepump for the circulation of heat-exchange fluid, due to the reduction inthe number of mechanisms within the energy storage and recovery system.

When a fluid (e.g., foam) is to either enter or exit the air chamber ofa pneumatic cylinder through a valve, it is desirable, as discussedearlier, that pressure drop through the valve be minimal, in order thatenergy losses entailed by passing through may be minimized. Furthermore,if the fluid to be passed through the valve is a foam, it may beadvantageous to minimize shear forces acting on the foam, in order toprevent the foam from being separated into its liquid and gascomponents, or in order to prevent the sizes of bubbles within the foamfrom being inadvertently altered. Moreover, where a liquid phase ispresent in the air chamber of a pneumatic cylinder as well as a gasphase (e.g., in cylinders employing foams for heat exchange betweenliquid and gas), it is desirable that valve check passively open toprevent damage to components from overpressure in the cylinder, i.e.,hydrolock events. Valve designs that enable high-efficiency, low-shearflow of foam with hydrolock protection are described in U.S. patentapplication Ser. No. 13/307,163, filed Nov. 30, 2011 (the '163application), the entire disclosure of which is incorporated byreference herein, and may be utilized in embodiments of the presentinvention.

FIG. 26 is a schematic representation of a pneumatic cylinder head 2600featuring two valves 2602, 2604 of types described in the '163application, a high-side valve 2602 and a low-side valve 2604. Thehigh-side valve 2602 is a pull-to-open valve that passively checks opento mitigate overpressure within the cylinder air chamber (i.e.,hydrolock). The low-side valve 2604 is a push-to-open valve thatpassively checks open when pressure is lower inside the cylinder thanoutside (e.g., during an intake stroke). Valves 2602 and 2604 may bedesigned for rapid action and with high lift (i.e., with a large areapermitting flow between the valve member and valve seat in the openposition) in order to minimize pressure drop through the valve (and thusenergy losses). High lift also reduces shear forces on foam flowing intoor out of the air chamber of the cylinder, preserving foam integrity.

FIG. 27 is a schematic diagram of portions of an illustrativecompressed-air energy-storage system 2700 that incorporates variousembodiments of the invention. The system 2700 includes a high-pressurepneumatic cylinder assembly 2702 (labeled HP in FIG. 27) that expandsand compresses gas between some mid pressure (e.g., approximately 200psig) and some high pressure (e.g., approximately 3,000 psig); alow-pressure pneumatic cylinder assembly 2704 that expands andcompresses gas between some low pressure (e.g., approximately 0 psig)and some mid pressure (e.g., approximately 200 psig); a mid-pressurevessel 2706 (labeled MPV in FIG. 27) that typically contains fluid(e.g., gas, heat-exchange liquid, foam, or separated gas and liquid) atthe mid pressure of the system; a storage reservoir 2708 orintercommunicating set of storage reservoirs (e.g., sealed lengths ofpiping rated for storage or transport of high-pressure gas) and capableof storing fluid at high pressure and mildly elevated temperature (e.g.,50° C.), and thus of acting as both a store of pressure potential energyand thermal energy; a storage vessel/spray reservoir 2710 (e.g., a tank)capable of holding an appropriate quantity of heat-exchange liquid at arelatively low temperature (e.g., 20° C.). The spray reservoir 2710preferably includes mechanisms for separating a low-pressure foam intoliquid and gas components and venting the gas component to theatmosphere (indicated by dashed arrow 2712). In FIG. 27, dashed arrowsrepresent the bidirectional movement of gas through appropriate pipingand solid arrows represent the bidirectional movement of liquid throughappropriate piping; pairs of dashed and solid arrows (2714, 2716, 2718,2720) indicate movement of gas and liquid between various components ofsystem 2700. The spray reservoir 2710 may exchange both liquid and gas(e.g., as separate flows of liquid and gas or as a single flow ofaqueous foam) with the low-pressure cylinder 2704, the low-pressurecylinder 2704 may exchange liquid and gas with the mid-pressure vessel2706, the mid-pressure vessel 2706 may exchange liquid and gas with thehigh-pressure cylinder 2702, and the high-pressure cylinder 2702 mayexchange liquid and gas with the high-pressure store 2708.

In FIG. 27, the high-pressure cylinder 2702, the mid-pressure vessel2706, and the low-pressure vessel 2704 are portions of a “power unit,”i.e., that subsystem of energy storage system 2700 which interconvertsthermal and pressure potential energy with mechanical work andelectrical energy. In a mode of operation where thermal and pressurepotential energy from warm, high-pressure fluid in the high-pressurestore 2708 are converted to electrical energy, a quantity of fluid istransferred from the high-pressure store 2708 to the high-pressurecylinder 2702. The fluid typically includes or consists essentially ofboth gas and liquid that are at approximately identical temperature andpressure. The gas and liquid may be combined into a foam prior toadmission to the high-pressure cylinder 2702 or may be foamed within thecylinder 2702. The cylinder 2702 expands its contents (e.g., foamsubstantially or entirely filling the air chamber of cylinder 2702) fromthe original high pressure (e.g., approximately 3,000 psig) to amid-pressure (e.g., 200 psig). As the gas component of the foam with thecylinder 2702 expands, performing work upon a moving piston withincylinder 2702, it tends to cool; however, as a temperature differenceappears between the gas and liquid components of the foam, thermalenergy flows from the liquid to the gas component. The larger thetemperature difference, the faster the flow of thermal energy fromliquid to gas will tend to be. Thus, the mingling of liquid and gas inan aqueous foam structure within cylinder 2702 will tend to allowsubstantially isothermal expansion of the gas component of the foam,effectively transforming a portion of the thermal energy in the liquidadmitted to cylinder 2702 into mechanical work.

When the contents of the cylinder 2702 have reached the mid-pressure ofthe system 2700, liquid and gas (e.g., as foam) at the mid-pressure aretransferred (arrows 2718) to the mid-pressure vessel 2706. Themid-pressure vessel stores the liquid and gas and may include provisionsfor regenerating foam or for separating foam into its gas and liquidcomponents. Whenever the mid-pressure vessel 2706 contains a sufficientquantity of gas at the mid-pressure, a quantity of gas is transferredfrom the mid-pressure vessel 2706 to the low-pressure cylinder 2704. Thegas is mingled with heat-exchange liquid from the mid-pressure vessel2706 to form a foam that substantially or entirely fills the air chamberof the low-pressure cylinder 2704. As in the high-pressure cylinder2702, only across a different pressure range, the gas within thelow-pressure cylinder 2704 is expanded, performing work upon a movingpiston with the cylinder 2704, as the liquid component of the foam tendsto make the expansion of the gas approximately isothermal. Afterexpansion of the gas in the low-pressure cylinder 2704, the liquid andgas within the cylinder 2704 are at relatively low temperature andapproximately atmospheric pressure, and are then transferred (arrows2714) to the spray reservoir and foam separator 2710. The low-pressuregas component of the foam is vented to the atmosphere (arrow 2712) andthe low-pressure liquid component of the foam is retained. If theretained liquid is cooler than the ambient (environmental) temperatureof the system 2700 at a time when the system 2700 is to be operated inan energy-generating mode, then the liquid in the spray reservoir 2710constitutes a store of energy (potential work), as does the store of hotliquid in the high-pressure store 2708. The storage reservoirs 2708 and2710 may be insulated in order to slow the loss of energy that occurs astheir contents warm or cool toward the temperature of the ambientenvironment. The number of compression and/or expansion stages, i.e., 2stages, depicted in FIG. 27 is illustrative. Additional expansion andcompression stages and mid-pressure vessels may be added to furtherdivide the pressure ranges (e.g., 3 compression/expansion stages—0 to 80psig, 80 psig to 500 psig, and 500 to 3000 psig, with mid-pressurevessels at approximately 80 psig and 500 psig).

Similarly, system 2700 may store energy by admitting atmospheric air(arrow 2712) and compressing it sequentially in cylinders 2704 and 2702.FIG. 28 shows a schematic representation of portions of the system 2700already depicted in FIG. 27, and attaches a time-versus-temperaturegraph 2800 to partially describe the stages of a hypothetical two-stagecompression. Pairs of thin lines converging from portions of graph 2800to portions of the schematic representation of system 2700 indicatewhich portions of graph 2800 represent changes in temperature occurringin which portions of system 2700. In graph 2800, dashed lines representthe temperature of gas, and solid lines represent the temperature ofheat-exchange liquid.

The graph 2800 begins at time T=0, the beginning of a compression strokein the low-pressure cylinder 2704. The cylinder contains a foam of whichthe gas and liquid components are both at the same low pressure(approximately atmospheric) and the same relatively low temperature(approximately 25° C.). From T=0 milliseconds (ms) to approximatelyT=290 ms, the foam is compressed in the cylinder 2704. The risingtemperature of the gas is represented by the dashed curve 2804. As thetemperature of the gas rises, heat is transferred to the liquidcomponent of the foam, whose temperature is represented by the solidcurve 2806. The curve 2804 clearly shows that the temperature of the gasis not constant, that is, that the compression of the gas is not purelyisothermal; however, it is substantially or approximately isothermal incomparison to the temperature change that would occur if the gasunderwent the compression adiabatically. In the adiabatic case, thetemperature of the gas would rise not to approximately 55° C., but toapproximately 295° C. Thus, the compression process undergone by the gasin cylinder 2704 may reasonably be termed “substantially isothermal,”with polytropic coefficient less than n=1.05, and realizes significantefficiency gains over the adiabatic case. These gains are not as largeas they would be for a perfectly isothermal compression (which wouldtake infinite time).

The difference between the solid line 2806 and dashed line 2805 (liquidand gas temperatures, respectively) represents lost energy that cannotbe recovered during a subsequent expansion. The minimization of thislost energy is achieved when the process time constant (in this case, acompression occurs in about 290 ms) is considerably less than theheat-transfer time constant. The heat-transfer time constant depends inpart on the surface area and proximity between the compressing orexpanding gas and the liquid. Small droplets or a foam matrix maximizethis surface area. In general, spheroidal droplets will have a lowersurface area than a matrix of foam cells; thus a foam matrix may resultin a lower heat transfer time constant, less lost energy, and a moreefficient energy storage system.

Graph 2800 in FIG. 28 shows that compression ceases at approximatelyT=290 ms, as the gas and liquid mixture is transferred to themid-pressure vessel. The gas quickly approximates the temperature of theliquid, as shown by the precipitous drop of dashed curve 2804 fromapproximately T=290 ms to approximately T=300 ms. The foam (and anyseparated liquid) in cylinder 2704 are then contained in themid-pressure vessel 2706. The foam may be regenerated within themid-pressure vessel at approximately constant pressure and temperature(depending on the size of the mid-pressure vessel, presumably sizedsufficiently large to prevent large fluctuations in pressure during asingle intake or exhaust from a LP or HP cylinder) and transferred tothe HP cylinder 2702. By approximately T=700 ms, the air chamber of theHP cylinder 2702 is filled substantially or entirely with foam and acompression stroke begins. Similarly to the compression in the LPcylinder 2704, the temperature of the gas component of the foam rises asshown by dashed curve 2810 (such temperature rise being significantlymitigated compared to the case of adiabatic compression), thetemperature of the liquid component of the foam rises as shown by solidcurve 2812, and the temperatures of the gas and liquid components of thefoam quickly equilibrate after compression ceases, as shown by theprecipitous drop in the dashed curve 2810 from approximately T=950 ms toapproximately T=1000 ms. The difference between the solid line 2812 anddashed line 2810 (liquid and gas temperatures, respectively) representslost energy that cannot be recovered during a subsequent expansion.Thereafter, the liquid and gas contents of the HP cylinder 2702 arestored within the high-pressure storage and thermal well 2708, remainingat approximately constant temperature and pressure as shown by solidcurve 2814.

The system 2700 thus uses heat-exchange liquid, foamed with gas duringexpansion and compression of the gas, both as an energy storage mediumand to enable rapid, approximately isothermal expansion and compressionof gas. Moreover, heat from a variety of external sources (e.g., solarheat, waste heat from fuel-burning power plants) may be transferred tothe fluid in reservoir 2708. Thermal energy thus added to fluid inreservoir 2708 may be partly realized as useful work in the cylinders2702 and 2704, and thus as electrical power output from the system 2700.In another embodiment, additional thermal energy may be transferred tothe fluid in storage 2708 in the form of low-grade heat from sourcessuch as power plants that would otherwise be wasted to the environmentas a form of cogeneration, further increasing or maintaining energyavailable during a subsequent expansion. Additionally, thermal energyfrom such sources of low-grade heat (not shown) may be transferred tothe mid-pressure vessel 2706 during expansion via heat exchanger (notshown) to increase recoverable energy.

FIG. 29 is a schematic diagram of portions of an illustrativecompressed-air energy-storage system 2900, similar in some respects tosystem 2700 in FIG. 27 and FIG. 28, that incorporates embodiments of theinvention. The system 2900 includes a high-pressure pneumatic cylinderassembly 2902 (labeled HP in FIG. 29) that expands and compresses gasbetween some mid pressure (e.g., approximately 200 psig) and some highpressure (e.g., approximately 3,000 psig); a low-pressure pneumaticcylinder assembly 2904 that expands and compresses gas between some lowpressure (e.g., approximately 0 psig) and some mid pressure (e.g.,approximately 200 psig); a mid-pressure vessel 2906 (labeled MPV in FIG.29) that typically contains fluid (e.g., gas, heat-exchange liquid,foam, or separated gas and liquid) at the mid pressure of the system; astorage reservoir 2908 or intercommunicating set of storage vessels(e.g., sealed lengths of piping rated for the storage or transport ofhigh-pressure gas) capable of storing fluid at high pressure andelevated temperature (e.g., 50° C.), and thus of acting as both a storeof pressure potential energy and thermal energy; a storage vessel/sprayreservoir 2910 (e.g., a tank) capable of holding an appropriate quantityof heat-exchange liquid at a relatively low temperature (e.g., 20° C.).The spray reservoir 2910 preferably includes mechanisms for separating alow-pressure foam into liquid and gas components and venting the gas tothe atmosphere (indicated by dashed arrow 2912). In FIG. 29, dashedarrows represent the bidirectional movement of gas through appropriatepiping and solid arrows represent the bidirectional movement of liquidthrough appropriate piping.

System 2900 also includes a high-pressure separation vessel 2922, whichfeatures one or more mechanisms for separating a foam (e.g., ahigh-pressure foam) into liquid and gas components. The storagereservoirs 2908, 2910, and 2926 may be insulated in order to slow theloss of energy that occurs as their contents warm or cool toward thetemperature of the ambient environment. The spray reservoir 2910 mayexchange both liquid and gas (e.g., as separate flows of liquid and gasor as a single flow of aqueous foam) with the low-pressure cylinder2904, the low-pressure cylinder 2904 may exchange liquid and gas withthe mid-pressure vessel 2906, the mid-pressure vessel 2906 may exchangeliquid and gas with the high-pressure cylinder 2902, the high-pressurecylinder 2702 may exchange gas with the high-pressure store 2908 and(via pump/motor 2924) liquid with the low-pressure thermal well 2926(e.g., insulated atmospheric pressure tank).

Like system 2700, system 2900 may be operated in either compression(energy-storage) or expansion (energy-generating) modes. During acompression mode of operation of system 2900, gas is compressedstagewise through the low-pressure cylinder 2904, the mid-pressurevessel 2906, and the high-pressure vessel 2902 as described above forsystem 2700. After compression in the HP cylinder 2902, liquid and gas(partly or substantially in the form of a foam) from the high-pressurecylinder 2902 are directed to the separation vessel 2922, where theliquid and gas components of the foam are separated by an appropriatemechanism (e.g., baffles, gravity, rotating blades, ultrasound,centrifuging, and/or other such mechanism). The separated gas componentof the foam is directed from the separation vessel 2922 to the storagevessel 2908; the separated heat-exchange liquid component, at relativelyhigh pressure (e.g., 3,000 psig) and high temperature (e.g., 50° C.) isdirected from the separation vessel 2922 through a pump/motor 2924 to alow-pressure storage vessel 2926 (e.g., a tank) capable of holding anappropriate quantity of heat-exchange liquid at elevated temperature andlow pressure. The pressure of the heat-exchange liquid is decreasedduring passage from the separation vessel 2922 through the pump/motor2924 to the storage vessel 2926, driving the pump/motor as a motor andthus generating useful energy (recovering this portion of the energyused during the compression of the liquid to elevated pressure). In analternative embodiment, the high-pressure storage reservoir 2908 may beused both as gas storage and as the liquid/gas separator, where liquidis removed from the low point of the gas storage reservoir after gravitydrainage of the liquid portion of the aqueous foam. In this embodiment,separation vessel 2922 is not a separate element from reservoir 2908. Inone embodiment, the storage reservoir 2908 is a horizontal pipe fieldwith large horizontal surface area which facilitates relatively rapidgravity drainage of an aqueous foam.

During an energy-generating (expansion) mode of operation of system2900, heat-exchange liquid at low pressure and possibly at elevatedtemperature from vessel 2926 is directed through pump/motor 2924.Pump/motor 2924, operated in pump mode, raises the pressure of theliquid to a level sufficient to permit the liquid's combination with gasat high pressure (e.g., approximately 3,000 psig) from the storagereservoir 2908 as a foam. The foam may be formed in the reservoir 2908,vessel 2922, in a mechanism distinct from the vessel 2922 and externalto the high-pressure cylinder 2902, or inside the high-pressure cylinder2902. Staged expansion of the gas in the HP cylinder 2902, mid-pressurevessel 2906, and low-pressure vessel 2904 then proceeds as describedabove for system 2700.

The system 2900 thus uses heat-exchange liquid, foamed with gas duringexpansion and compression of the gas, both as an energy storage mediumand to enable rapid, substantially isothermal expansion and compressionof gas. Unlike system 2700, system 2900 does not use a single vessel (orinterconnected set of vessels) to store both high-pressure gas andheat-exchange liquid. This has the advantage that a smaller volume ofhigh-pressure storage is required; the total volume of storage requiredon the hot side of the system 2900 (i.e., the storage of both hot liquidin vessel 2926 and hot, high-pressure gas in vessel 2908) isapproximately the same as for system 2700, but since vessel 2926 islow-pressure it is likely to be lower-cost per unit volume thanhigh-pressure vessel 2908.

Moreover, heat from a variety of external sources (e.g., solar heat,waste heat from fuel-burning power plants) may be transferred to theliquid in thermal well 2926 with relative ease (compared to transferringheat to the contents of high-pressure stores 2700 or 2908), sinceheat-exchange mechanisms tolerating high pressures will not be neededfor such heat harvesting. Thermal energy thus added to thermal well 2926may be partly realized as useful work in the cylinders 2902 and 2904,and thus as cogenerated electrical power output from the system 2900.Lower total storage cost and/or cogeneration may more than compensatefor the energy loss entailed by transferring high-pressure liquid fromthe separation vessel 2922 to a low pressure in thermal well 2926 incompression modes and by pumping low-pressure liquid from thermal well2926 to a high pressure for foaming with gas in the HP cylinder 2902during expansion modes.

During a generation mode of a compressed-gas energy storage systememploying storage reservoirs of fixed volume for storage ofhigh-pressure gas, gas is progressively exhausted, continuously or inbatches, from a high-pressure storage reservoir in order that itspotential energy may be partly realized as mechanical and electricalenergy. During such progressive exhaustion of the high-pressure store,the pressure and temperature of the gas within the store will tend todecrease in an approximately adiabatic manner. As will be apparent topersons familiar with the principles of thermodynamics, thisapproximately adiabatic pressure and temperature decrease will entail aloss of recoverable energy due to lower available pressures and/or anenergy loss due to temperature mixing. Similarly, during a storage modeof the compressed-gas energy storage system, gas is progressivelydelivered, continuously or in batches, to the high-pressure storagereservoir in order that its potential energy may be stored. During suchprogressive delivery of gas to the high-pressure store, the pressure andtemperature of the gas within the store will tend to increase in anapproximately adiabatic manner, with corresponding increased work tocompress to higher pressure and/or mixing energy loss due to mismatchedtemperatures.

To prevent energy losses during either exhaustion of gas from ordelivery of gas to the high-pressure store, it may be desirable tomaintain heat exchange between gas undergoing either compression orexpansion within the high-pressure store and a heat-exchange liquid.Heat exchange between gas and liquid in the high-pressure store may beachieved by partly or substantially filling the high-pressure store withfoam, where the liquid component of the foam is a heat-exchange liquid.The liquid component of the foam will tend to either give up thermalenergy to the gas component of the foam, or to absorb thermal energyfrom the gas component, enabling approximately isothermal increase ordecrease of pressure within the high-pressure store during either astorage or generation mode of operation of the system. The temperatureof the liquid component of the foam, or of the foam mixture may befurther altered by a heat-exchange mechanism (heat exchanger) externalto the high-pressure store, shedding heat from the environment orharvesting heat from the environment or some source of cogenerativeheat. Either foam or separated liquid may be circulated through a heatexchanger external to the high-pressure store. In other embodiments,heat-exchange mechanisms (e.g., finned tubes) may be provided internallyto the high-pressure store, so that an external heat-exchange fluid(e.g., environmental air) may be circulated into the high-pressure storewithout mingling with its contents, rather than contents of thehigh-pressure being circulated to an external heat exchanger. Techniquesfor heat exchange with a compressed gas stored in a gas-onlyhigh-pressure store are described in U.S. patent application Ser. No.13/094,960, filed Apr. 27, 2011 (the '960 application), the entiredisclosure of which is incorporated by reference herein. Theminimization of this lost energy is achieved when the process timeconstant is considerably less than the heat-transfer time constant. Ingeneral, a compression or expansion within the storage reservoir occursat a much slower time constant than within the cylinders and power unit.For example, compression of gas from 750 psig to 3,000 psig in a storagereservoir may take approximately one hour. The heat-transfer timeconstant depends in part on the surface area and proximity between thecompressing or expanding gas and the liquid. Small droplets or a foammatrix maximize this surface area. In general, spheroidal droplets willhave a lower surface area than a matrix of foam cells; thus, a foammatrix may result in a lower heat-transfer time constant, less lostenergy, and a more efficient energy storage system. For the storagereservoir heat exchange, a lower quality foam or low quality orintermittent spray or circulation may be sufficient to achieve thedesired heat transfer time constant (e.g., substantially lower timeconstant than 1 hour).

FIG. 30 is a schematic representation of an illustrative mechanism forcirculating fluid from a high-pressure store in order to achieveapproximately isothermal changes in pressure in the store during theexhaustion of gas from or delivery of gas to the store, or to add energyto the gas within the store from a cogenerative or other source throughthe use of a heat exchanger. Fluid from the reservoir (3002 a-3002 d) iscirculated through a heat exchanger 3004 using a pump 3006 operating asa circulator. The circulated fluid may be gas, or heat-exchange liquid,or a foam including both gas and liquid. The pump 3006 operates with asmall pressure change sufficient for circulation, but within a housingthat is able to withstand high pressures, as detailed in the '409application. The pump 3006 circulates the high-pressure fluid throughthe heat exchanger 3004 without substantially increasing its pressure(e.g., a 50 psi increase for 3,000 psi air). The fluid is thenre-injected into the reservoir 3002 a-3002 d, possibly through amechanism that regenerates a foam or other two-phase mixture (e.g.,spray of droplets) within the reservoir 3002 a-3002 d. In this way, thetemperature of the stored compressed gas may be controlled (e.g.,raised, lower, held approximately constant, or held approximately equalto the internal liquid temperature) by opening valve 3008 with valve3010 closed and heated during expansion (release of gas form thereservoir 3002 a-3002 d) or cooled during compression (delivery of gasto the reservoir 3002 a-3002 d) by closing valve 3008 and opening valve3010. Valve 3010, when open, places the subsystem 3000 in fluidcommunication with an energy-storage system such as system 2700 in FIG.27. The heat exchanger 3004 may be any sort of standard heat-exchangerdesign; illustrated in FIG. 30 is a tube-in-shell type heat exchangerwith high-pressure air inlet and outlet ports 3012 and 3014 andlow-pressure shell ports 3016 and 3018 (which may be connected to anexternal heating or cooling source).

In other embodiments, foam is circulated from reservoir 3002 a-3002 dthrough heat exchanger 3004. The fluid circulated through the externalloop of heat exchanger 3004 may, in various embodiments, be a gas,liquid, or foam. The reservoir 3002 a-3002 d is depicted in FIG. 30 in ahorizontal position but other orientations are contemplated and withinthe scope of the invention.

FIG. 31 is a schematic of an illustrative alternative compressed-airstorage reservoir subsystem 3100 for heating and cooling of compressedgas in energy storage systems in order to expedite transfer of thermalenergy to and from the compressed gas prior to and/or during expansionor compression. As depicted, thermal energy transfer to and from storedfluid in storage reservoirs 3102, 3104 is expedited via liquidcirculation using a pump 3106. The liquid pump 3106 operates with asmall pressure change sufficient for circulation and spray (and/or foamgeneration), but within a housing that is able to withstand highpressures; that is, it circulates high-pressure water (or other suitableheat-transfer fluid) through heat exchanger 3108 and introduces theliquid into storage reservoirs 3102 and 3104 without substantiallyincreasing its pressure (e.g., a 50 psi increase for circulating andspraying within 3,000 psig stored compressed gas). The heat exchangermay be omitted or bypassed in other embodiments. The heat exchanger 3108may be any sort of standard heat exchanger design; illustrated here is atube-in-shell heat exchanger with high-pressure liquid inlet and outletports 3112 and 3114 and low-pressure shell liquid ports 3116 and 3118.The shell ports 3116 and 3118 may permit communication with a secondheat exchanger, a thermal well, or some other body of fluid.

Heat exchange within the storage reservoirs 3102, 3104 is expedited byactive spraying or foaming of liquid (e.g., water) into the vessels3102, 3104. Herein, “spraying” refers to any passage of liquid through amechanism (e.g., small orifice, engineered nozzle, mechanism directing aspray against an impingement pin or plate) that acts upon the liquidmechanically in such a manner as to divide the liquid into droplets.“Foaming” refers to any passage of liquid through a mechanism thatmingles it with gas to form a foam; such mechanisms include schemeswhere the liquid is directed against a surface producing or acted uponby ultrasound, which surface vibrates the liquid in such a way as toproduce breakup or foaming. All such mechanisms are contemplated andwithin the scope of the invention. The illustrative system of FIG. 31shows multiply perforated rods (spray rods) as the spray/foamingmechanism. As illustrated in FIG. 31, perforated rods 3120 and 3122 maybe installed inside storage reservoirs 3102 and 3104. The perforatedrods 3120, 3122 may be located along or at the top of the storagereservoirs 3102, 3104, along the middle portion of the storagereservoirs (as illustrated in FIG. 31), and/or along the bottom of thestorage reservoirs (e.g., a sparging type arrangement). The rods 3120,3122 may extend through part or all of the length of the storagereservoirs 3102, 3104. The pump 3106 increases the liquid pressure abovethe reservoir pressure such that liquid is actively circulated andsprayed/foamed out of rods 3120, 3122, as shown by arrows 3124 and 3126.With spraying and/or foaming into storage reservoirs 3102 and 3104,droplets or foam matrices of the liquid within the gas inside storagereservoirs 3102, 3104 occurs, enabling efficient heat transfer betweenthe liquid and the gas. Foam may partially or substantially fill thestorage reservoirs 3102, 3104. Over time, the foam will tend toseparate, producing accumulations of liquid 3128, 3130 at the bottom ofthe storage reservoirs 3102, 3104. Liquid thus accumulated may beremoved through ports 3132, 3134 and associated piping 3136. The piping3136 returns the liquid to the heat exchanger 3108, through which theliquid 3128, 3130 is circulated as part of the closed-loop watercirculation and spray/foaming system. Valve 3110, when open, places thesubsystem 3100 in fluid communication with an energy-storage system suchas system 2700 in FIG. 27.

In various other embodiments, foam or gas is circulated from storagereservoirs 3102, 3104 through heat exchanger 3108. The fluid circulatedthrough the external loop of heat exchanger 3108 may, in variousembodiments, be a gas, liquid, or foam. The ports 3132, 3134 may belocated on the top or sides of storage reservoirs 3102, 3104 such as topull gas (e.g., in a sparging arrangement) or foam instead ofpreferentially pulling separated liquid. The storage reservoirs 3102,3104 and their internal spray mechanisms 3120, 3122 are depicted in FIG.31 in a horizontal position but other orientations are contemplated andwithin the scope of the invention. Two storage reservoirs 3102, 3104 aredepicted in FIG. 31 but other numbers of storage reservoirs, such as,e.g., pipelines and natural or artificial caverns are contemplated andwithin the scope of the invention.

FIG. 32 is a schematic of an alternative compressed-air storagereservoir subsystem 3200 for heating and cooling of compressed gas inenergy storage systems, to expedite transfer of thermal energy to andfrom the compressed gas prior to and/or during expansion or compression.Thermal energy transfer to and/or from stored compressed gas in storagereservoirs 3202 is expedited via fluid circulation using an enclosure3204 and air circulation fans 3206. The storage reservoirs 3202 may alsoinclude heat-exchange liquid, which may be separated or mingled with thegas in the storage reservoirs 3202 to form a foam that partially orentirely fills the storage reservoirs 3202. Separated liquid, foam, andgas not incorporated in a foam may coexist in the storage reservoirs3202 and in all other high-pressure storage reservoirs depicted herein.In the subsystem 3200, fluid (e.g., air) enters the enclosure 3204through intake openings (e.g., vents) 3208. The fluid may be at atemperature different from the compressed gas within the storagereservoirs 3202. The storage reservoirs 3202 are in an arrangement thatpermits substantial circulation of fluid around and between them. Fluidcirculating around and between the storage reservoirs 3202 gains thermalenergy from the storage reservoirs 3202 if the fluid entering throughthe vents 3208 is at a lower temperature than the fluid within thestorage reservoirs 3202; similarly, the storage reservoirs 3202 gainthermal energy from the fluid entering through the vents 3208 if thecirculating fluid is at a higher temperature than the fluid within thestorage reservoirs 3202. Fluid that has circulated around and betweenthe storage reservoirs 3202 is typically pulled from the enclosure 3204by exhaust devices (e.g., pumps, fans) 3206, represented illustrativelyin FIG. 32 as fans. The gas exhausted by devices 3206 may be confined byone or more ducts (not shown), circulated through a heat-exchange systemto change its temperature, and returned to the vents 3208 through theducts. The exterior of the enclosure 3204 may be insulated. The fluidentering the intake openings 3208 may be heated or cooled and thuschange the temperature of storage reservoirs 3202 and their interiorcontents. The source of such heating may be waste heat from a sourcesuch as a thermal power plant or industrial process, and may be a directsource such as solar heating or fuel fired heating elements.

Valves and piping (not shown) may place the contents of the storagereservoirs 3202 in fluid communication with an energy-storage systemsuch as system 2700 in FIG. 27. The storage reservoirs 3202 are depictedin FIG. 32 in a horizontal position but other orientations arecontemplated and within the scope of the invention. Six storagereservoirs 3202 are depicted in FIG. 32 but other numbers of storagereservoirs, as well as other types of gas storage, are contemplated andwithin the scope of the invention.

FIG. 33 is a schematic of yet another compressed-air storage reservoirsubsystem 3300 for use with heating and cooling of compressed gas inenergy storage systems, to expedite transfer of thermal energy to andfrom the compressed gas prior to and/or during expansion or compression.Thermal energy transfer to and from stored compressed gas in storagereservoirs 3302 is expedited via circulation of one or more fluids(e.g., water, aqueous foam) in an enclosure 3304 and using piping 3306,3308 to respectively admit fluid to and remove fluid from the enclosure3304. The storage reservoirs 3302 may also contain heat-exchange liquid,which may be separated or mingled with the gas in storage reservoirs3302 to form a foam that partially or entirely fills the storagereservoirs 3302. In the exemplary subsystem 3300 depicted in FIG. 33,the fluid level 3310 in enclosure 3304 is indicated by closely-spacedvertical lines. Fluid enters the enclosure 3304 through pipe 3306. Thefluid may be at a temperature different from that of the fluid withinthe storage reservoirs 3302. The storage reservoirs 3302 are preferablyin an arrangement that permits substantial circulation of water (orother fluid) around and between them. Fluid circulating around andbetween the storage reservoirs 3302 gains thermal energy from thestorage reservoirs 3302 if the fluid entering through pipe 3306 is at alower temperature than the fluid within the storage reservoirs 3302;similarly, the storage reservoirs 3302 gain thermal energy from thefluid if the fluid entering through the pipe 3306 is at a highertemperature than the fluid within the storage reservoirs 3302. Fluidthat has circulated around and between the storage reservoirs 3302 isremoved from the enclosure through pipe 3308. The fluid removed throughpipe 3308 may be circulated through a heat-exchange system (not shown inFIG. 33) to change its temperature and returned to the enclosure 3304through pipe 3306.

Valves and piping (not shown) may place the contents of the storagereservoirs 3302 in fluid communication with an energy-storage systemsuch as system 2700 in FIG. 27. The storage reservoirs 3302 are depictedin FIG. 33 in a horizontal position but other orientations arecontemplated and within the scope of the invention. Six storagereservoirs 3302 are depicted in FIG. 33 but other numbers of storagereservoirs are contemplated and within the scope of the invention.

FIG. 34 illustrates another compressed-air storage reservoir subsystem3400 for heating and cooling of compressed gas in energy-storagesystems, to expedite transfer of thermal energy to and from thecompressed gas prior to and/or during expansion or compression. Thermalenergy transfer to and from stored compressed gas in a pressurizedreservoir such as a cavern 3402 (e.g., a naturally occurring orartificially created cavern, which may be located underground) isexpedited via liquid circulation using a liquid pump 3404 and heatexchanger 3406. The cavern 3402 may also contain heat-exchange liquid,which may be separated or mingled with the gas in the cavern 3402 toform a foam that partially or entirely fills the cavern 3402. Liquid orfoam 3420 may pool at the bottom of the cavern 3402. The pump 3404operates with a small pressure change sufficient for circulation andspray/foam generation, but within a housing that is able to withstandhigh pressures; pump 3404 circulates high-pressure fluid through heatexchanger 3406 and then to a spray/foam-generation mechanism 3408,creating a foaming spray 3410 inside the cavern 3402 withoutsubstantially increasing the pressure of the fluid (e.g., a 50 psiincrease for circulating and spraying within 3,000 psi stored compressedair). In this way, the stored compressed gas may be pre-heated (orpre-cooled) using a fluid circulation and spraying/foaming method, whichalso may allow for active liquid monitoring of the storage cavern 3402.The two-phase heat exchange may occur as pre-heating prior to expansionand/or pre-cooling prior to compression. The circulation may be donewithout heat exchanger 3406 and serve to maintain the heat exchangeliquid and gas at substantially the same temperature during an expansionor compression. The pump 3404 may be submerged in the liquid or foam3420 or be external to the liquid or foam 3420. The heat exchanger 3406may be of any standard heat-exchanger design; illustrated here is atube-in-shell heat exchanger with high-pressure liquid inlet and outletports 3412 and 3414 and low-pressure shell liquid ports 3416 and 3418.The shell ports 3416 and 3418 may permit communication with a secondheat exchanger or a thermal well or some other body of fluid.

Heat exchange within the storage cavern 3402 is expedited by activespraying and foam generation 3410 of liquid (e.g., water with one ormore foaming additives) into the cavern 3402. Illustrated in FIG. 34 isa scheme where one or more perforated spray heads 3408 are installedwithin the storage cavern 3402. Pump 3404 increases the fluid pressureabove the cavern pressure such that fluid is actively circulated andsprayed out of spray head 3408. Foam may partially or entirely fill thevolume of cavern 3402. Due to foam separation, liquid and/or foam 3420may accumulate at the bottom of the cavern 3402 and be removed throughpiping 3422. The piping 3422 returns the liquid and/or foam 3420 to thepump 3404 and heat exchanger 3406, through which the liquid and/or foamis circulated as part of the closed-loop fluid circulation andfoam-generation and/or foam-regeneration system. A valve or valves andpiping (not shown) may place cavern 3402 in fluid communication with anenergy-storage system such as system 2700 in FIG. 27.

If the cavern 3402 is of sufficient size, a substantial mass of liquidand/or foam 3420 may be allowed to accumulate at the bottom of thecavern 3402. In this case, this mass of liquid and/or foam 3420 mayexchange heat relatively slowly with the air also contained in cavern3402, and may be used as a thermal reservoir.

A vertical cavern shape and spray-head-type internal foam-generationmechanism 3408 are depicted in FIG. 34 but other orientations and sprayor foam-generation mechanisms (e.g., spray rod, multiple nozzles) arecontemplated and within the scope of the invention. The spray head 3408may be located at the bottom of the cavern to allow sparging of air intothe accumulating liquid and/or foam 3420 to form or regenerate a foamwithin the cavern 3402. A single cavern 3402 is depicted in FIG. 34 butother numbers of caverns and storage reservoirs featuring both cavernsand other forms of gas storage (e.g., pressure vessels and/or pipes) arecontemplated and within the scope of the invention.

FIG. 35 is a diagram of various components of an energy storage andrecovery system in accordance with various embodiments of the invention.The illustrated system includes or consists essentially of aninstallation 3500 where thermal energy is available for recovery,extracted from the surroundings, needed for usage, and/or may be removedfor cooling. Example installations 3500 include fossil-fuel based powerplants (e.g., coal, natural gas); other heat-engine based power plantssuch as nuclear, solar thermal, and geothermal; industrial processeswith waste heat; heat pumps, heat sources, and heat sinks; buildingsneeding space heating or cooling; and sources of environmentally chilledwater. In FIG. 35, for illustrative purposes, a power plant 3502 isshown whose excess thermal energy is recoverable through a standardheat-exchange unit 3504. Generated power 3506 from the power plant 3502may be used to drive the compressed-gas energy storage system 3508 asdetermined by the operator (e.g., when market demand for power is low),storing energy in the form of compressed gas in storage reservoir 3510.Energy may be additionally stored as the thermal energy or energy ofliquids cooled below the environmental temperature or warmed above it,and these liquids may be located in the same vessels that contain thecompressed gas (e.g., mingled with it as a foam) or separated from thegas and stored in separate vessels. Upon demand for increased power,this stored energy undergoes expansion (e.g., staged expansion) in thecompressed-gas energy storage system 3508 to generate power for usage(e.g., power grid delivery 3512). The recovered thermal energy from thepower plant 3502 may be used in the heat-exchange subsystem of thecompressed-gas storage reservoir 3510 (or other pressurized storage) topreheat the stored compressed gas and/or to heat the heat-exchange fluidand gas before or during expansion and/or between expansion/compressionstages in mid-pressure vessels, increasing the work done by a givenvolume of pressurized gas and improving system efficiency and/orperformance. Likewise, but not illustrated herein, water cooled by heatexchange with cold environments, ground loops, water loops, or otherlow-temperature reservoirs may be used in the heat-exchange subsystem topre-cool and/or continually cool the compressed gas prior to and duringfurther compression, improving system efficiency and/or performance. Inall these instances, performance and/or value of the system may bemarkedly improved.

FIG. 36 depicts an illustrative system 3600 that substantiallyisothermally compresses or expands gas over a predetermined pressurerange in accordance with various embodiments of the present invention.System 3600 includes a cylinder 3602 containing a mobile piston 3604 (orother suitable boundary mechanism) that divides the interior of thecylinder 3602 into a gas-filled chamber (also termed air chamber orpneumatic chamber) 3606 (and a liquid-filled, i.e., hydraulic) chamber3608. Alternatively, chamber 3608 may be gas-filled, and/or the airchamber 3606 may contain one or more of gas, liquid, and foam. Anintegrated heat-exchange mechanism is typically present in chambers 3606and/or 3608, as described in the '155 patent and/or as shown in FIG. 2.In the illustrative embodiment shown in FIG. 36, a spray head 3610injects a spray 3612 of fluid into the upper chamber 3606 of thecylinder 3602. This spray 3612 may include or consist essentially of anaqueous foam comprising both gas and a heat-exchange liquid, or of aliquid that mixes with gas in the air chamber 3606 to form an aqueousfoam. Foam 3614 partially or entirely fills the air chamber 2606;partial separation of the foam 3614 may also occur, allowing liquid toaccumulate on top of piston 3604. Ports 3620 and 3630 with valves 3622and 3632 allow gas to be admitted to or exhausted from chamber 3606 asdesired. A port or ports (not shown) with associated pipes and valves(not shown) allow fluid to be admitted to or withdrawn from chamber 3608as desired.

During air expansion, the gas in chamber 3606 expands, performing workon piston 3604. As the gas in chamber 3606 expands, its temperaturetends to fall, and thermal energy is transferred from to the gas fromthe heat-transfer liquid within chamber 3606 (e.g., the liquid componentof a foam partly or wholly filling chamber 3606). The transfer ofthermal energy to the gas from the liquid in chamber 3606 increases theamount of work performed by the expanding gas on the piston 3604. As thegas in chamber 3606 expands, its temperature tends to fall, and thermalenergy is transferred from to the gas from the heat-transfer liquidwithin chamber 3606 (e.g., the liquid component of a foam partly orwholly filling chamber 3606). The transfer of thermal energy to the gasfrom the liquid in chamber 3606 increases the amount of work performedby the expanding gas on the piston 3604.

During air compression, piston 3604 moves upward and thus compresses thegas in chamber 3606. As the gas in chamber 3606 is compressed, itstemperature tends to rise, and thermal energy is transferred from thegas to the heat-transfer liquid within chamber 3606 (e.g., the liquidcomponent of a foam partly or wholly filling chamber 3606). The transferof thermal energy from the gas to the liquid in chamber 3606 decreasesthe amount of work that the piston 3604 must perform on the expandinggas. The transfer of thermal energy to the liquid from the gas inchamber 3606 reduces the amount of work that the piston 3604 performs onthe gas in chamber 3606 in order to compress the gas.

To prepare the cylinder 3602 for compression, low-pressure gas isadmitted from point 3634 through valve 3632 and port 3630 into upperchamber 3606 during a downward stroke starting with piston 3604 near orat the top of cylinder 3602. The gas may be mingled with liquid to forma foam, either before, during, or after admission to chamber 3606. Invarious embodiments of the invention, the inlet pressure at point 3634is raised above atmospheric pressure by a blower (e.g., lobe type) orpump/compressor (e.g., screw pump) 3642 that draws inatmospheric-pressure or near-atmospheric-pressure gas through inlet/vent3640. The compression by pump/compressor 3642 may be predominantlyadiabatic; alternatively, pump/compressor 3642 may include, e.g., ascrew pump that permits the introduction of a heat-exchange foam and/ordroplets into air undergoing compression and/or expansion within screwpump 3642, enabling the substantially isothermal compression and/orexpansion of air within screw pump 3642. The foam may be subsequentlypumped by the screw pump 3642 to chamber 3606. Moreover, as shown inFIG. 36, the screw pump 3642 may be a bidirectional expander/compressor;hence, references herein to “compressor 3642” and “expander 3642” belowmay refer to a single bidirectional screw-pump unit. The outlet of thecompressor 3642 may be attached to a low-pressure vessel 3650 near or atthe predetermined minimum system pressure at point 3634 (i.e., thesuper-atmospheric pressure enabled by the compressor 3642 and thatserves as the inlet pressure to cylinder 3602) in order thatlow-pressure vessel 3650 may provide a buffer such that the compressor3642 may operate continuously at near-constant power. The low-pressurevessel 3650 may contain integrated heat exchange as described above andin the '155 patent. At or near the bottom of a downward (intake) strokepreparatory to compression, where piston 3604 is at or near the bottomof cylinder 3602 and chamber 3606 is filled with gas (and/or foam) at apredetermined pressure by the action of compressor 3642 and valve 3632,valve 3632 is closed. An upward compression stroke follows. At apredetermined high pressure, which may be equal to the pressure at point3624 (e.g., the pressure in a high-pressure storage reservoir likereservoir 222 or higher-pressure cylinder in a multi-stage system),valve 3622 is opened, connecting chamber 3606 through port 3620 to point3624. The pressurized gas and/or foam is then forced through valve 3622to point 3624, until piston 3604 is near or at the top of cylinder 3606,whereupon valve 3622 closes and the process repeats with another intakestroke.

In comparison to a system otherwise identical to system 3600 but lackinga compressor 3642, the presence of the compressor 3642 in system 3600enables a greater amount (mass) of gas to be compressed in a singleupstroke of piston 3604 within cylinder 3602. The work of compressiondone in a single stroke with compressor 3642 is higher than withoutcompressor 3642 and more gas is compressed to point 3624.

The efficiency of the total compression for predominantly adiabaticcompression by compressor 3642 and substantially isothermal compressionin the cylinder 3602 is typically less than a substantially isothermalcompression completely within the cylinder 3602 over the entire pressurerange, as previously mentioned. The efficiency of the total compressionfor substantially isothermal compression by compressor 3642 andsubstantially isothermal compression in the cylinder 3602 is alsotypically less than a substantially isothermal compression completelywithin the cylinder 3602 over the entire pressure range. The addition ofthe compressor 3642 thus generally increases the power of system 3600(i.e., the rate at which system 3600 transforms work to potential energyof compressed gas) at the expense of efficiency. The degree of tradeoffbetween power and efficiency that is optimal typically varies dependingon the application in which system 3600 is used. Additionally, for agiven outlet pressure at port 3620, the higher starting pressure withinchamber 3606 of the cylinder 3602 reduces the pressure range (ratio ofoutlet pressure to inlet pressure) over which the cylinder 3602 actsduring the course of a stroke; as reviewed above, this also narrows therange of forces that act on rod 3618 that is attached to the piston 3604and whose nether end extends out of cylinder 3602. This narrowing of therange of forces in turn enables more efficient conversion of electricalenergy by a motor/generator (not shown) to work in the system 3600, aspreviously discussed.

During an expansion, a predetermined amount of compressed gas and/orfoam at high pressure is admitted from point 3624 (e.g., from a storagevessel such as reservoir 222 in FIG. 2 or higher-pressure cylinder in amulti-stage system such as system 2700 in FIG. 27) through valve 3622and port 3620 into chamber 3606. The amount of gas and/or foam admittedmay be set by a control system (e.g., controls system 122 in FIG. 1)such that after fully expanding on a downward stroke (i.e., when piston3604 reaches the bottom of cylinder 3602), the gas and/or foam reaches apredetermined minimum system pressure that is typicallysuper-atmospheric (e.g., approximately 5 psig). For example, the controlsystem may be responsive to one or more sensors measuring gas flow rateand/or pressure within cylinder 3602 to meter the gas introduction. Onthe upward return stroke of the cylinder 3602, that gas is exhaustedthrough valve 3632 to point 3634.

In various embodiments of the invention, the piping at point 3634 isattached to an expander 3642 that converts the pressurized gas flow intorotational motion; in such embodiments, gas flow through the expander3642 generates power additional to the amount generated by the expansionwithin the cylinders. The expansion through the expander 3642 may bepredominantly adiabatic; alternatively, expander 3642 may permit theintroduction of a heat-exchange foam and/or droplets into air undergoingexpansion within expander 3642, enabling the substantially isothermalexpansion of air within expander 3642. After expansion through theexpander 3642, the gas (or gaseous component of foam) may be exhaustedto the atmosphere through vent 3640. In addition, as shown in FIG. 36, alow-pressure vessel 3650 near or at the predetermined minimum systempressure (i.e., the super-atmospheric pressure input to the expander3642 and that serves as the outlet pressure of cylinder 3602) may alsobe connected at point 3634 in order to provide a buffer such that theexpander 3642 may operate continuously at near-constant power. Asmentioned above, the low-pressure vessel 3650 may contain an integratedheat-exchange mechanism.

By ending the expansion stroke within cylinder 3602 at a pressure aboveatmospheric pressure, a greater amount (mass) of gas may be expanded ina single downstroke of piston 3604 within cylinder 3602. The work ofexpansion done in that single stroke (higher forces acting over adistance) will be higher than the amount of work performed by anotherwise identical stroke during which a smaller amount of gas isexpanded (lower forces acting over the same distance). Moreover, if anexpander 3642 is employed, additional power may be generated that wouldbe lost if the super-atmospheric-pressure gas in chamber 3606 at the endof an expansion stroke were vented directly to the atmosphere. The totalefficiency of a predominantly adiabatic expansion in expander 3642combined with a predominantly isothermal expansion in cylinder 3602 istypically less than the efficiency of a near-isothermal expansioncompletely within the cylinder 3602 over the entire pressure range. Theefficiency of the total expansion for substantially isothermal expansionby expander 3642 and substantially isothermal expansion in the cylinder3602 is also typically less than a substantially isothermal expansioncompletely within the cylinder 3602 over the entire pressure range. Theemployment of super-atmospheric venting pressure combined with anexpander 3642 thus generally adds power at the expense of efficiency.The degree of tradeoff between power and efficiency that is optimaltypically varies depending on the application in which system 3600 isused. Additionally, the higher vent pressure of the cylinder 3602reduces the pressure range over which the cylinder 3602 acts for a givenoutlet pressure (i.e., where range is outlet/inlet pressure), such thatsome benefit of efficiency of power transmission may be achieved byoperating the cylinder 3602 over a narrower pressure (and thus force)range.

A control system (e.g., control system 122 in FIG. 1) may control thecompressor/expander 3642 and cylinder 3602 in order to enforcesubstantially isothermal expansion and/or compression of gas in cylinder3602 over a particular range of super-atmospheric pressures andsubstantially adiabatic compression and/or expansion inexpander/expander 3642 between approximately atmospheric pressure andthe minimum super-atmospheric pressure of operation of cylinder 3602.For example, the control system may direct the introduction of gasand/or foam into and the exhausting of gas and/or foam out of cylinder3602 and expander/expander 3642 via, e.g., control over the variousports and/or valves associated with these components. The control systemmay be responsive to one or more sensors disposed in or on cylinder 3602and/or expander/expander 3642 for measuring the pressure of the gaswithin these components, and direct movement of the gas within system3600 accordingly. As described above, control of substantiallyisothermal compression and/or expansion within cylinder 3602 may alsoentail control over an associated heat-transfer subsystem that may foamheat-exchange liquid with the gas. Such heat-transfer subsystems may beturned off or rendered idle during substantially adiabatic orsubstantially isothermal compression and/or expansion inexpander/expander 3642.

FIG. 37 depicts an illustrative system 3700 that substantiallyisothermally compresses or expands gas over a predetermined pressurerange in accordance with various embodiments of the present invention.System 3700 employs the same substantially isothermal cylinder stageshown in system 3600 of FIG. 36, but features a separate and parallelset of control valves and other components for expansion andcompression. System 3700 includes a cylinder 3702 containing a mobilepiston 3704 that divides the interior of the cylinder 3702 into agas-filled (pneumatic) chamber 3706 and a liquid-filled (hydraulic)chamber 3708. Alternatively, both chambers 3706 and 3708 may begas-filled. An integrated heat-exchange mechanism may be present inchambers 3706 and/or 3708, as described in the '155 patent and/or asshown in FIG. 36. In the illustrative embodiment, a spray head 3710forms a spray 3712 of heat-exchange liquid, thereby forming a foam withthe gas in the upper chamber 3706 of the cylinder 3702. In otherembodiments, the spray head 3710 may be located outside the cylinder3702. This spray 3712 may produce an accumulation of liquid 3714 on topof piston 3704. Ports 3720 and 3730 with valves 3722 and 3732 allow gasto be admitted to or exhausted from chamber 3706 as desired. A port orports (not shown) with associated pipes and valves (not shown) allowsfluid to be admitted to or withdrawn from chamber 3708 as desired.

During air expansion, gas and/or foam in chamber 3706 expands,performing work on piston 3704. As the gas in chamber 3706 expands, itstemperature tends to fall. If during expansion the spray 3712 enterschamber 3706 at a suitable temperature (e.g., the temperature of the gasin chamber 3706 before compression begins), then the liquid component ofthe foam is at a higher temperature during expansion than the gas inchamber 3706, and the liquid component of the foam transfers thermalenergy to the gas in chamber 3706. The transfer of thermal energy fromthe liquid component of the foam to the gas in chamber 3706 increasesthe amount of work performed by the expanding gas on the piston 3704. Ineffect, this transfer of thermal energy from the liquid component of thefoam to the gas in chamber 3706 enables the conversion of some of thethermal energy in the spray 3712 into work.

During air compression, piston 3704 moves upward and thus compresses thegas in chamber 3706. While the gas in chamber 3706 is being compressedby the piston 3704, its temperature tends to rise. If during compressionthe liquid spray 3712 enters chamber 3706 at a suitable temperature(e.g., the temperature of the gas in chamber 3706 before compressionbegins), then the gas in chamber 3706 is at a higher temperature duringcompression than the liquid component of the foam, and the gas inchamber 3706 transfers thermal energy to the liquid component of thefoam. The transfer of thermal energy to the liquid component of the foamfrom the gas in chamber 3706 reduces the amount of work that the piston3704 must perform on the gas in chamber 3706 in order to compress thegas.

During a downward stroke (preparatory to a compression stroke) startingwith piston 3704 near or at the top of cylinder 3702, low-pressure gasis admitted from point 3734 through valve 3730 (shown here as a checkvalve) and through port 3730 into upper chamber 3706. In variousembodiments of the invention, the inlet pressure at point 3734 is raisedabove atmospheric pressure by a compressor 3740 (e.g., a screw pump3740) drawing in atmospheric or near-atmospheric pressure gas throughinlet/vent 3741. The compression by compressor 3740 may be predominantlyadiabatic; alternatively, compressor 3740 may permit the introduction ofa heat-exchange foam and/or droplets into air undergoing compressionwithin compressor 3740, enabling the substantially isothermalcompression of air within compressor 3740. As shown in the illustrativeexample of FIG. 37, the compressor 3740 need not be a bidirectionalexpander/compressor, but may be implemented as a unidirectional devicethat may be turned off or rendered idle during expansion mode. Theoutlet of the compressor 3740 may include an after-cooler or otherheat-exchange system (not shown) and may be attached to a low-pressurevessel 3750 near or at the predetermined minimum system pressure atpoint 3734 in order to provide a buffer such that the compressor 3740may operate continuously at substantially constant power duringcompression mode. The low-pressure vessel 3750 may contain integratedheat exchange as described above. At or near the bottom of a downwardstroke, where piston 3704 is at or near the bottom of cylinder 3702,chamber 3706 is filled with fluid (e.g., foam) at the predeterminedpressure by the action of compressor 3740 and valve 3730, valve 3730 isclosed, and an upward compression stroke is performed. Alternatively, asshown, valve 3730 operates as a check valve and closes as soon as theupward compression stroke pressurizes chamber 206 above the pressure atpoint 3734. At a predetermined high pressure, preferably equal to thepressure at point 3724 (e.g., from a storage reservoir such as reservoir222 or a higher-pressure cylinder in a multi-stage system), valve 3720(shown here as a check valve) is opened, connecting chamber 3706 throughport 3720 to point 3724. The pressurized fluid is then forced throughvalve 3720 to point 3724, until piston 3704 is near or at the top ofcylinder 3706, when valve 3720 closes and the process repeats withanother intake stroke. Alternatively, as shown in FIG. 37, valve 3720operates as a check valve and opens as soon as the upward compressionstroke pressurizes chamber 3706 above the pressure at point 3724 andcloses as soon as the downward intake stroke begins, reducing pressurein chamber 3706 below the pressure at point 3724.

Using the compressor 3740, a greater amount (mass) of gas may becompressed in a single upstroke of piston 3704 within cylinder 3702 thanmay be compressed without using compressor 3740. The work of compressiondone in that single stroke will be higher than without compressor 3740and more gas will be compressed to point 3724. The efficiency of thetotal compression for a predominantly adiabatic compression incompressor 3740 and a predominantly isothermal compression in cylinder3702 tends to be less than for a substantially isothermal compressioncompletely within the cylinder 3702 over the entire pressure range. Theefficiency of the total compression for substantially isothermalcompression by compressor 3740 and substantially isothermal compressionin the cylinder 3702 is also typically less than a substantiallyisothermal compression completely within the cylinder 3702 over theentire pressure range. The addition of the compressor 3740 thustypically adds power at the expense of efficiency. Additionally, thehigher super-atmospheric starting pressure within the cylinder 3702reduces the pressure range over which the cylinder 3702 acts for a givenoutlet pressure (i.e. where range is outlet/inlet pressure), such thatsome benefit of efficiency of power transmission may be achieved byoperating the cylinder 3702 over a narrower pressure (and thus force)range.

During expansion, a predetermined amount of compressed gas at highpressure is admitted from point 3724 (e.g. from a storage reservoir suchas reservoir 222 or a higher-pressure cylinder in a multi-stage system)through valve 3722 and port 3720 into chamber 3706. As illustrated inFIG. 37, valve 3722 may be a unidirectional valve, i.e., optimized forflow in only one direction. The amount of gas admitted may be set by thecontrol system 122 such that after fully expanding on a downward stroke(i.e., piston 3704 reaches the bottom of cylinder 3702) the gas reachesthe predetermined minimum system pressure for cylinder compressionand/or expansion (e.g. approximately 5 psig). On the upward returnstroke of the cylinder 3702, that gas is exhausted through valve 3732 topoint 3736. In various embodiments of the invention, point 3736 may beattached to an expander 3742 that converts the pressurized gas flow torotational motion, performing work and generating additional power abovethe amount generated by the expansion within the cylinder(s). As shownin the illustrative example, the expander 3742 need not be abidirectional expander/compressor, but may be implemented as aunidirectional expander that may be turned off or rendered idle duringcompression mode. The expansion through the expander 3742 may bepredominantly adiabatic, such as that achieved by a centrifugal oraxial-turbine-type expander; alternatively, expander 3742 may permit theintroduction of a heat-exchange foam and/or droplets into air undergoingexpansion within expander 3742, enabling the substantially isothermalexpansion of air within expander 3742. After expansion through theexpander 3742, the gas may be exhausted to atmosphere through vent 3741.In addition, as shown in this illustrative embodiment, a low-pressurevessel 3752 near or at the predetermined minimum system pressure mayalso be connected at point 3736 in order to provide a buffer such thatthe expander 3742 may operate continuously at substantially constantpower. The low-pressure vessel 3752 may contain integrated heat exchangeas described above.

By ending the expansion stroke within cylinder 3702 at a pressure aboveatmospheric pressure, a greater amount (mass) of gas may be expanded ina single downstroke of piston 3704 within cylinder 3702. The work ofexpansion done in that single stroke is typically higher than that donewith less gas. Additionally, with an expander 3742, additional power maybe generated that would be lost if the super-atmospheric-pressure gaswere vented directly to atmosphere. The efficiency of the totalexpansion for a predominantly adiabatic expansion in expander 3750 and apredominantly isothermal expansion in cylinder 3702 may be less than asubstantially isothermal expansion completely within the cylinder 3702over the entire pressure range. The efficiency of the total expansionfor substantially isothermal expansion by expander 3742 andsubstantially isothermal compression in the cylinder 3702 is alsotypically less than a substantially isothermal compression completelywithin the cylinder 3702 over the entire pressure range. The addition ofthe higher vent pressure thus typically adds power at the expense ofefficiency. The degree of tradeoff between power and efficiency that isoptimal typically varies depending on the application in which system3700 is used. (For example, at certain low pressures, the cost of anexpander may not be worth the recovered power; in such a case, vessel3752 and expander 3742 may be profitably omitted.) Additionally, thehigher vent pressure of the cylinder 3702 typically reduces the pressurerange over which the cylinder 3702 acts for a given outlet pressure; asa result, the benefit of efficiency of power transmission may beachieved by operating the cylinder 3702 over a narrower pressure (andthus force) range.

Additionally, the higher vent pressure at port 3730 reduces the pressurerange (ratio of outlet pressure to inlet pressure) over which thecylinder 3702 acts during the course of a stroke; this also narrows therange of forces that act on rod 3718. This narrowing of the range offorces in turn enables more efficient conversion of work performed bysystem 3700 to electrical energy by a motor/generator (not shown).

Reference is now made to FIG. 38, which depicts another illustrativeembodiment of the invention. A volume 3800 (e.g., pipeline, fluidreservoir, gas reservoir, pneumatic chamber filled with gas or foam)contains fluid at a pressure P_(s). Due to frictional losses and workperformed in creating fluid motion, this pressure P_(s), may be lowerthan the pressure P_(i) at which the fluid was injected into the volume3800. Alternatively or additionally, pressure P_(i) may simply be somepressure, higher than P_(s), to which it is desired to raise fluidextracted from volume 3800. In order to continuously pump the fluid backinto the volume 3800, or into another volume 3804 at any pressure (e.g.,P) higher than P_(s), a screw pump 3802 may be installed as a boosterpump, symbolized in FIG. 38 by a cartoon of a screw pump. The screw pump3802 efficiently takes inlet fluid from the volume 3800 at pressureP_(s), and outputs fluid at pressure P_(i) for injection back intovolume 3800 or into a second volume 3804 (as depicted in FIG. 38).

A screw pump may be employed as a booster or circulation pump in any ofthe illustrative mechanisms depicted herein that employs a booster orcirculation pump. In such applications, the screw pump may featureapparatus that permits the introduction of a heat-exchange foam and/ordroplets into air undergoing compression and/or expansion within screwpump, enabling the substantially isothermal compression and/or expansionof air within screw pump. The foam thus generated may be transported bypiping from the screw pump to a pneumatic cylinder, separator, storagereservoir, or other component of the energy storage system.

FIG. 39 depicts an illustrative system 3900 that features a power unit3902 (including a cylinder assembly unit for compression and expansionof gas), a cylinder heat-exchange system 3904, a vent 3905 to draw airfrom and exhaust air to the environment, a storage reservoir 3906capable of holding fluid (e.g., air and/or water) at high pressure(e.g., 3,000 psi), a thermal well 3908 for storage and retrieval ofthermal energy (e.g., a body of water), a waste-heat heat-exchangesystem 3910 coupled to waste heat generated by mechanical and/orelectronic components of the power unit 3902, and an environmentalheat-exchange system 3912 for exchanging thermal energy with theenvironment (e.g., the air, the ground). Lines 3914, 3916, 3918, 3919,3920, 3922, 3924, and 3926 denote piping, valves, and other arrangementsfor exchange of gas, liquid, and/or thermal energy between thecomponents the lines connect. The cylinder heat-exchange system 3904features components for generating or otherwise processing foams and/orsprays, for changing the pressure of fluids, and for routing fluidtransfers between the various components with which the cylinderheat-exchange system 3904 is in fluid communication (e.g., store 3906,power unit 3902, thermal well 3908); the cylinder heat-exchange systemsdepicted in subsequent figures may include components performing similarfunctions. In FIG. 39 and subsequent figures, the power unit 3902 isdepicted as including a single spray- or foam-cooled pneumatic cylinder(at top) connected to a crankshaft, seen in cross-section; however, thisdepiction is illustrative and conceptual only, and is not intended torestrict the mechanisms that might be employed in system 3900 (or inother illustrative systems depicted herein) for the interconversion ofthermal, gas elastic potential, mechanical, and electrical energy. Inother embodiments, not depicted herein, the power unit 3902 includesmultiple cylinders, and interconversion of mechanical and electricalenergy may occur via hydraulic systems, linear generators, and otheralternatives to the cylinder-crankshaft combination depicted in FIG. 39and some other figures herein. Moreover, in various embodiments, thewater employed as a heat-exchange and thermal-energy-storage material insystem 3900 includes one or more additives, or is replaced by adifferent fluid (e.g., an oil). Also, materials other than water,including non-fluid or multiphase materials (e.g., aqueous foams), maybe employed as the energy-storage medium of the thermal well 3908. Thedepictions of power units, heat-exchange liquids, and thermal wells inall figures herein are illustrative and nonrestrictive. Moreover, in allillustrative systems described herein, environmental heat-exchange unitsand waste-heat heat-exchange units are optional wherever depicted.

Possible modes of operation of system 3900 include an expansion mode anda compression mode. In the compression mode, a quantity of gas (e.g.,air) at relatively low (e.g., atmospheric) pressure is admitted at anambient or moderate temperature to the cylinder assembly in power unit3902. The compression of the gas in the cylinder assembly is maintainedsubstantially isothermal by introduction into the gas of a spray offoaming liquid drawn from the thermal well 3908 via the heat-exchangesystem 3904, thereby forming a foam in the power unit 3902. The water inthe thermal well 3908 is here presumed to be at a relatively low (e.g.,ambient) temperature at the beginning of the compression-mode cycle, andmay include one or more foaming additives (alternatively, theadditive(s) may be added by the heat-exchange system 3904). The liquidcomponent of the foam undergoing compression may be returned via thecylinder heat-exchange system 3904 to the thermal well 3908 at a highertemperature than the water was drawn from the thermal well 3908, havinggained thermal energy during compression. At or near the end of eachcompression stroke of the cylinder assembly, gas at high pressure andapproximately ambient temperature is conveyed through piping to thehigh-pressure reservoir 3906.

Throughout a single cylinder compression cycle, or throughout a seriesof cylinder compression cycles, return of heated water to the thermalwell 3908 will generally tend to raise the temperature of the water inthe thermal well 3908. If thermal well 3908 is a single body of water,then the temperature of that body will tend to rise; if the thermal well3908 includes one or more hot-water reservoirs and one or morecold-water reservoirs, the temperature of the water in the one or morehot-water reservoirs (and thus the average temperature of the contentsof thermal well 3908) will tend to rise. In effect, some energy thatoriginated as mechanical work performed on gas undergoing compression inthe power unit 3902 will be stored as thermal energy in the thermal well3908.

In the expansion mode of system 3900 (e.g., an expansion cyclesubsequent to the compression cycle described hereinabove), gas at highpressure may be transferred from the reservoir 3906 to the cylinder ofthe power unit 3902, where it expands, performing work on a piston. Asor before the gas expands within the cylinder, foamable liquid may betransferred from the thermal well 3908 to the power unit 3902 via thecylinder heat-exchange system 3904. This liquid (e.g., water with one ormore additives) may be at a relatively high temperature due to thetransfer of thermal energy to the thermal well 3908 during priorcompression cycles or by other processes. Water from the thermal well3908 forms a foam with the gas undergoing expansion, transferring heatto the gas as the gas cools and thus tending to keep the expansionsubstantially isothermal and causing the gas to perform more work on thepiston. In effect, thermal energy stored in the thermal well 3908 may beconverted to work in the power unit 3902 during an expansion cycle ofsystem 3908. Thermal energy stored in the thermal well 3908 may comefrom compression cycles of the power unit 3902, or from other sources;in particular, the waste-heat heat-exchange unit 3910 may be employed totransfer heat from the mechanical and electrical components of powerunit 3902 to the thermal well 3908. Heat from other sources, not shownin FIG. 39, may also be transferred to the thermal well 3908.

The temperature of the thermal well 3908 may be decreased or heldconstant despite the addition of heat thereto (e.g., via the cylinderheat exchange system 3904) by shedding heat from the thermal well 3908to the environment (e.g., atmosphere or ground) via an environmentalheat-exchange unit 3912. Waste heat from the power unit 3902 may also beshed via the environmental heat-exchange unit 3912. For example, if atthe end of a series of expansion cycles the temperature of the waterwithin the thermal well 3908 is not sufficiently low for use in asubsequent series of compression cycles, heat may be shed from thethermal well 3908 to the environment via environmental heat-exchangeunit 3912 during an inactive interval, i.e., a period when reservoir3906 contains stored pressurized gas but system 3900 is not beingemployed as a generator. An environmental heat-exchange unit 3912 thatis designed to allow system 3900 to shed unwanted heat slowly during aninactive interval will tend to be smaller and less costly than onedesigned to shed heat quickly (in real time) during active operation ofsystem 3900, reducing the cost of system 3900. The use of a thermal well3908 enables the time-shifting of waste thermal energy to theenvironment, which may have the advantage of both making theenvironmental heat-exchange unit smaller due to lengthening the timeover which a certain amount of thermal energy is dissipated and alsoallowing the heat exchange to potentially take place at times differentfrom the operation times of the power unit, which may allow usage atmore optimal environmental temperatures (e.g., colder night temperaturesfor dissipating heat). Moreover, unwanted heat from the reservoir 3906,gas undergoing compression in the power unit 3902, and heat frommechanical and electronic inefficiencies of the power unit 3902 may allbe shed to the environment by the single environmental heat-exchangeunit 3912, realizing further cost and simplicity advantages overcomparable systems that utilize multiple heat-exchange units to controlthe temperature of various subsystems.

During gas-expansion cycles of system 3900, the temperature of thethermal well 3908 may be increased or held constant despite the removalor loss of heat from the thermal well 3908 by adding heat to the thermalwell 3908 harvested from the environment via the environmentalheat-exchange unit 3912. During gas-compression cycles, the temperatureof the thermal well 3908 may be decreased or held constant despite theaddition of heat to the thermal well 3908 by shedding heat from thethermal well 3908 to the environment via the environmental heat-exchangeunit 3912. Such temperature management of the thermal well 3908 may bedesirable for efficiency reasons or, for example, to keep the water inthe thermal well 3908 from either freezing or boiling.

Transferring energy to the thermal well 3908 from foam undergoingcompression in a series of compression cycles will generally tend toproduce a body of high-temperature water for use in a subsequent seriesof expansion cycles; transferring energy out of the thermal well 3908 tofoam undergoing expansion in a series of expansion cycles will generallytend to produce a body of low-temperature water for use in a subsequentseries of compression cycles. By maintaining a generallyhotter-than-ambient reservoir of liquid in the thermal well 3908 forspraying during or before expansions, and a generallycooler-than-ambient reservoir of liquid in the thermal well 3908 forspraying during or before compressions, the efficiency of the energystorage and generation system 3900 may be increased over that of anotherwise comparable system whose foaming liquid is always ambient intemperature. Moreover, obtaining higher and lower temperature extremesin the thermal well 3908 by storing thermal energy obtained from gasundergoing compression and expansion, rather than by using heaters,refrigeration, or heat-pump devices to obtain the desired temperatureextremes, may reduce parasitic energy expenditures and consequentlyincrease the overall efficiency of the system 3900.

Capture of heat from mechanical and electronic inefficiencies in thepower unit 3902 via the waste-heat heat-exchange unit 3910, and thetransfer of such heat to thermal well 3908 for partial conversion towork in subsequent expansion cycles, will typically also tend toincrease the overall efficiency of the system 3900.

In some embodiments, the thermal well 3908 includes a vessel (not shown)for the storage of liquid at high pressure and high temperature;additionally or alternatively, liquid at high pressure and temperaturemay be stored in the vessel 3906 along with gas at high pressure andhigh temperature. These and other bodies of high-temperature liquid maybe employed during expansion cycles of system 3900 to achievesubstantially isothermal gas compression.

FIG. 40 depicts an illustrative system 4000 that features a power unit4002, a cylinder heat-exchange system 4004, a vent 4005 to draw andexhaust air from and to the environment, a storage reservoir 4006capable of holding fluid (e.g., air and water) at high pressure (e.g.,3,000 psi), a thermal well 4008 for storage and retrieval of thermalenergy (e.g., a body of water), a waste-heat heat-exchange system 4010coupled to waste heat generated by mechanical and electronic componentsof the power unit 4002, an environmental heat-exchange system 4012capable of exchanging thermal energy with the environment (e.g., theair, the ground), a spray-liquid (for foam generation) reservoir 4028,and a spray-to-well heat-exchange unit 4030 fluidly coupled on one sideto the thermal well 3908 and on the other to the spray reservoir 4028.System 4000 may also include an optional secondary environmental heatexchange unit 4032.

Possible modes of operation of system 4000 include an expansion mode anda compression mode. In the compression mode, a quantity of gas (e.g.,air) at relatively low (e.g., atmospheric) pressure is admitted at anambient or moderate temperature to the cylinder assembly of power unit4002 from vent 4005 via piping 4019. The compression in the cylinderassembly is kept substantially isothermal by introduction into the gasof a spray of foaming liquid (e.g., water with one or more additives)drawn from the spray reservoir 4028 via the spray-to-well heat-exchangeunit 4030 and the cylinder heat-exchange system 4004, thereby forming afoam in the cylinder assembly. The water in the spray reservoir 4028 ishere presumed to be at a relatively low (e.g., ambient) temperature. Thewater sprayed through the gas undergoing (and/or prior to) compressionmay be returned via the cylinder heat-exchange system 4004 to the sprayreservoir 4028 at a higher temperature than the water was drawn fromspray reservoir 4028, having gained thermal energy from the gasundergoing compression. The temperature of the water in spray reservoir4028 will typically thus tend to be increased by compression cycles ofthe power unit 4002. However, as water from spray reservoir 4028 passesthrough the spray-to-well heat exchanger 4030, heat may be transferredfrom the spray fluid to the thermal well 4008, reducing the temperatureof the spray fluid. Heat added to the spray reservoir 4028 bycompression cycles of the power unit 4002 may thus be transferred duringsubsequent compression cycles to the thermal well 4008, allowing thetemperature of the spray liquid in reservoir 4028 to be keptapproximately constant.

System 4000 may realize advantages already described hereinabove forsystem 3900 in FIG. 39, including temperature management of the contentsof thermal well 4008 and partial conversion to work of waste heat frompower unit 4002. Additionally, in system 4000, the thermal-storageliquid in the thermal well 4008 does not mix with the spray liquid, andthe quantity of liquid in the thermal well 4008 may be significantlylarger than the quantity of spray liquid. Separation of thermal-storageliquid and spray liquid in system 4000 may be advantageous because anyliquid sprayed inside the power unit 4002 is preferably maintained in astate of relatively high purity (notwithstanding the presence of one ormore foaming additives) so that spray contaminants do not degrade theperformance of components of the power unit 4002. The thermal-storageliquid in system 4000 is not sprayed inside the power unit 4002 andtherefore need not be maintained in as high a state of purity as thespray liquid. Maintenance of a relatively small volume of spray liquidin a state of high purity is generally less costly than maintaining therelatively large volume of the thermal well 4008 in a state of highpurity, as would be preferable if the contents of the thermal well 4008were to be used as spray liquid (as the contents of thermal well 3908are in system 3900). Moreover, the spray liquid may contain additivesthat may be omitted from the thermal-storage liquid, another opportunityfor economic gain in the operation of system 4000 as compared tooperation of system 3900. Additionally, heat exchanger 4030 may beembedded in the thermal well 4008 and the contents of the thermal well4008 may be solid (e.g., gravel), a phase-change material (e.g.,paraffin wax), or some other thermal-storage material (e.g., oil,ceramics).

FIG. 41 depicts an illustrative system 4100 that features a power unit4102 (including a cylinder assembly unit for compression and expansionof gas), cylinder heat-exchange system 4104, a vent 4105 to draw andexhaust air from and to the environment, a storage reservoir 4106capable of holding fluid (e.g., air and water) at high pressure (e.g.,3,000 psi), a hot thermal well 4108 (e.g., thermally insulated body ofwater), a cold thermal well 4113 (e.g., a second thermally insulatedbody of water), a waste-heat heat-exchange system 4110 coupled to wasteheat generated by mechanical and electronic components of the power unit4102, a waste-to-well heat-exchange system 4112 coupled on one side tothe hot thermal well 4108 and on the other side to the waste-heatheat-exchange system 4110, a first environmental heat-exchange system4132 capable of exchanging thermal energy with the environment (e.g.,the air, the ground), and a second environmental heat-exchange system4136 also capable of exchanging thermal energy with the environment.

Possible modes of operation of system 4100 include an expansion mode anda compression mode. In the compression mode, a quantity of gas (e.g.,air) at relatively low (e.g., atmospheric) pressure is admitted fromvent 4105 at an ambient or moderate temperature to the cylinder assemblyof power unit 4102. The compression is maintained substantiallyisothermal by introduction into the gas of a spray of water drawn fromthe cold thermal well 4113 via the cylinder heat exchange system 4104,thereby forming a foam within the cylinder assembly. The water thussprayed through the gas undergoing or prior to compression may bereturned via the cylinder heat-exchange system 4104 to the hot thermalwell 4108 at a higher temperature than the water was drawn from coldthermal well 4113, having gained thermal energy from the gas undergoingcompression. Water will therefore tend to be transferred from the coldthermal well 4113 to the hot thermal well 4108 during compression cyclesof the power unit 4102.

Similarly, in the expansion mode of system 4100, a quantity of gas(e.g., air) at relatively high pressure (e.g., 3,000 psi) is admitted atan ambient or moderate temperature to the cylinder assembly of powerunit 4102. The expansion is maintained substantially isothermal byintroduction into the gas of a spray of water drawn from the hot thermalwell 4108 via the cylinder heat exchange system 4104, thereby forming afoam within the cylinder assembly. The water thus sprayed into the gasduring expansion may be returned via the cylinder heat exchange system4104 to the cold thermal well 4113 at a lower temperature than the waterwas drawn from hot thermal well 4108, the sprayed water having impartedthermal energy to the gas undergoing expansion. Water will thereforetend to be transferred from the hot thermal well 4108 to the coldthermal well 44113 during expansion cycles of the power unit 4102.

The environmental heat exchangers 4132 and 4136 enable the temperaturesof the thermal wells 4108, 4113 to be managed in both expansion andcompression modes as already described hereinabove for the thermal wellsof systems 3900 and 4000. Heat from the waste-heat heat-exchange unit4110 may be transferred to the hot thermal well 4108 by means of thewaste-to-well heat-exchange system 4112 or to the environment by meansof an additional environmental heat exchange system (not shown).

System 4100 may realize advantages already described hereinabove forsystems 3900 and 4000, including temperature management of the contentsof thermal wells 4108, 4113 and partial conversion to work of waste heatfrom power unit 4102. Further, it will be apparent to persons reasonablyfamiliar with the principles of thermodynamics that the maintenance oftwo thermal wells 4108, 4113 at (preferably) distinct temperaturesdecreases the entropy (due to mixing of hot and cold streams) andincreases the energy (extractable work) of system 4100, making theoperation of system 4100 potentially more efficient than the operationof a system (e.g., system 4000) having only a single thermal well.Moreover, heat may be added to the hot thermal well 4108 from any sourcewithout altering the temperature of the cold thermal well 4113, and heatmay be transferred out of the cold thermal well 4113 (e.g., byenvironmental heat exchanger 4136) without altering the temperature ofthe hot thermal well 4108.

FIG. 42 depicts an illustrative system 4200 that features a power unit4202 (including a cylinder assembly unit for compression and expansionof gas), a cylinder heat-exchange system 4204, a vent 4205 to draw andexhaust air from and to the environment, a storage reservoir 4206capable of holding fluid (e.g., air and water) at high pressure (e.g.,3,000 psi), a hot thermal well 4208 (e.g., thermally insulated body ofwater), a cold thermal well 4234 (e.g., a second thermally insulatedbody of water), a waste-heat heat-exchange system 4210 that extractswaste heat generated by mechanical and electronic components of thepower unit 4202, a waste-to-well heat-exchange system 4212 coupled onone side to the hot thermal well 4208 and on the other to the waste-heatheat-exchange system 4210, a spray reservoir 4228, a spray-to-wellheat-exchange unit 4230 fluidly coupled on one side to the hot thermalwell 4208 and cold thermal well 4234 and on the other side to the sprayreservoir 4228, a first environmental heat-exchange system 4232 capableof exchanging thermal energy with the environment (e.g., the air, theground), and a second environmental heat-exchange system 4236 alsocapable of exchanging thermal energy with the environment.

Possible modes of operation of system 4200 include an expansion mode anda compression mode. In the compression mode, a quantity of gas (e.g.,air) at relatively low (e.g., atmospheric) pressure is admitted fromvent 4205 at an ambient or moderate temperature to the cylinder assemblyof power unit 4202. The compression is maintained substantiallyisothermal by introduction into the gas of a spray of water drawn fromthe spray reservoir 4228 via the spray-to-well heat exchanger 4230 andthe cylinder heat exchange system 4204, thereby forming a foam withinthe cylinder assembly. The water in the spray reservoir 4228 is herepresumed to be at a relatively low (e.g., ambient) temperature at thebeginning of the compression-mode cycle. The water thus sprayed throughthe gas undergoing or prior to compression may be returned via sprayheat-exchange unit 4204 to the spray reservoir 4228 at a highertemperature than the water was drawn from spray reservoir 4228, havinggained thermal energy from the gas undergoing compression. Thetemperature of the water in spray reservoir 4228 will thus tend to beincreased by compression cycles of the power unit 4202. However, asspray liquid from spray reservoir 4228 passes through one side of thespray-to-well heat exchanger 4230 on its way to the spray heat-exchangeunit 4204, heat may be transferred from the spray liquid to thermal-wellliquid passing from the cold thermal well 4234 to the hot thermal well4208 through the other side of the spray heat-exchange unit 4230,reducing the temperature of the spray liquid and tending to increase thetemperature of the liquid in the hot thermal well 4208. Thermal energyadded to the spray reservoir 4228 by compression cycles of the powerunit 4202 may thus be transferred during subsequent compression cyclesto the hot thermal well 4208, and the temperature of the spray liquid inreservoir 4228 may thus be kept substantially constant.

Similarly, in an expansion mode of system 4200, a quantity of gas (e.g.,air) at relatively high pressure (e.g., 3,000 psi) is admitted at anambient or moderate temperature to the cylinder assembly of power unit4202. The expansion is maintained as substantially isothermal byintroduction into the gas of a spray of water drawn from the sprayreservoir 4228 via the spray-to-well heat-exchange unit 4230 and thecylinder heat exchange system 4204, thereby forming a foam within thecylinder assembly. The water in the spray reservoir 4228 is herepresumed to be at a relatively high (e.g., approximately 60° C., or evenhigher) temperature at the beginning of the compression-mode cycle. Thewater thus sprayed through the gas undergoing or prior to compressionmay be returned via spray heat-exchange unit 4204 to the spray reservoir4228 at a lower temperature than the water was drawn from sprayreservoir 4228, having imparted thermal energy to the gas undergoingexpansion. The temperature of the water in spray reservoir 4228 willthus tend to be decreased by compression cycles of the power unit 4202.However, as spray liquid from spray reservoir 4228 passes through oneside of the spray-to-well heat exchanger 4230, heat may be transferredto the spray liquid from fluid passing from the hot thermal well 4208 tothe cold thermal well 4234 through the other side of the spray-to-wellheat exchanger 4230, increasing the temperature of the spray liquid anddecreasing the temperature of the liquid being moved from the hotthermal well 4208 to the cold thermal well 4234. Heat removed from thespray reservoir 4228 by expansion cycles of the power unit 4202 may thusbe restored during each subsequent compression cycle by extracting heatfrom the hot thermal well 4208, and the temperature of the spray liquidin reservoir 4228 may be kept approximately constant.

The environmental heat exchangers 4232 and 4236 enable the temperaturesof the thermal wells 4208, 4234 to be managed in both expansion andcompression modes as already described hereinabove for the thermal wellsof systems 3900 and 4000. The directions of flow through heat exchanger4230 may be reversed when switching between compression and expansionmode via additional valving and piping (not shown) to maintaincounterflow. Also, heat from the waste-heat heat-exchange unit 4210 maybe transferred from the power unit 4202 to the hot thermal well 4208 bymeans of the waste-to-well heat-exchange system 4212.

System 4200 may realize advantages already described hereinabove forsystems 3900, 4000, and 4100, including temperature management of thecontents of thermal wells 4208, 4234 and partial conversion to work ofwaste heat from power unit 4202. Further, it will be apparent to personsreasonably familiar with the principles of thermodynamics that themaintenance of two thermal wells 4208, 4234 at (preferably) distincttemperatures decreases the entropy and increases the energy (extractablework) of system 4200, making the operation of system 4200 potentiallymore efficient than the operation of a system (e.g., system 4000) havingonly a single thermal well. As in system 4100, heat may be added to thehot thermal well 4208 from any source without altering the temperatureof the cold thermal well 4234 or of the spray reservoir 4228, and heatmay be transferred out of the cold thermal well 4234 (e.g., byenvironmental heat exchanger 4236) without altering the temperature ofthe hot thermal well 4208 or of the spray reservoir 4228. Additionally,in system 4200, the thermal-storage liquid in the thermal wells 4208,4234 does not mix with the spray liquid, and the quantity of liquid inthe thermal wells 4208, 4234 may be significantly larger than thequantity of spray liquid. Separation of thermal-storage liquid and sprayliquid in system 4200 may be advantageous because any liquid sprayedinside the power unit 4202 is preferably maintained in a state ofrelatively high purity so that spray contaminants do not degrade theperformance of components of the power unit 4202. The thermal-storageliquid in system 4200 is not sprayed inside the power unit 4202 andtherefore need not be maintained in as high a state of purity as thespray liquid. Maintenance of a relatively small volume of spray liquidin a state of high purity is generally less costly than maintaining therelatively large volume of the thermal wells 4208, 4234 in a state ofhigh purity. Moreover, the spray liquid may contain additives that maybe omitted from the thermal-storage liquid, another opportunity foreconomic gain in the operation of system 4200 (as compared to, e.g.,operation of system 4100). Additionally, heat exchanger 4230 may beembedded in the thermal well 4208 and/or 4234 and the contents of thethermal well 4208 and/or 4234 may be solid (e.g., gravel), aphase-change material (e.g., paraffin wax), or some otherthermal-storage material (e.g., oil, ceramics).

FIG. 43 depicts an illustrative system 4300 that features a power unit4302 (including a cylinder assembly unit for compression and expansionof gas), a cylinder heat-exchange system 4304, a storage reservoir 4306capable of holding both gas and liquid at high pressure (e.g., 3,000psi) and relatively high temperature, a waste-heat heat-exchange system4310 coupled to waste heat generated by mechanical and electroniccomponents of the power unit 4302, a waste-to-well heat-exchange system4312 coupled on one side to the high-pressure fluid reservoir 4306 andon the other side to the waste-heat heat-exchange system 4310, a coldthermal well 4334 including or consisting essentially of, e.g., a bodyof water, a first environmental heat-exchange system 4332 capable ofexchanging thermal energy with the environment (e.g., the ground), and asecond environmental heat-exchange system 4338 also capable ofexchanging thermal energy with the environment. The high-temperature,high-pressure reservoir 4306 combines functions of a high-pressure gasstore with functions of a hot thermal well and may be a single unit(e.g., insulated pressure tanks, insulated pipelines, undergroundgeologic formation such as salt domes).

Possible modes of operation of system 4300 include an expansion mode anda compression mode. In the compression mode, a quantity of gas (e.g.,air) at relatively low (e.g., atmospheric) pressure is admitted fromvent 4305 at an ambient or moderate temperature to the cylinder assemblyof power unit 4302. The compression of the gas is maintainedsubstantially isothermal by introduction into the gas of a spray ofwater drawn from the cold thermal well 4334 via the cylinder heatexchange system 4304, thereby forming a foam within the cylinderassembly. The water thus sprayed into the gas undergoing or prior tocompression may be directed, along with the compressed gas, via thecylinder heat-exchange system 4304 to the high-temperature,high-pressure reservoir 4306 at a higher pressure and temperature thanthe water was drawn from cold thermal well 4334, having gained thermalenergy from the gas undergoing compression. Water will therefore tend tobe transferred from the cold thermal well 4334 to the high-temperature,high-pressure reservoir 4306 during compression cycles of the power unit4302.

Similarly, in the expansion mode of system 4300, a quantity of gas(e.g., air) at relatively high pressure (e.g., 3,000 psi) and relativelyhigh temperature is transferred from the high-temperature, high-pressurereservoir 4306 to the cylinder assembly of power unit 4302. As thecylinder assembly expands the gas, the temperature of the gas tends todecrease; the degree of this decrease is limited by the foam formationwith the gas, and the expansion is preferably maintained substantiallyisothermal. In the expansion mode of system 4300, the spray liquidincludes or consists essentially of water (e.g., with one or morefoaming additives) drawn from the high-temperature, high-pressurereservoir 4306 via the cylinder heat-exchange system 4304. At the end ofan expansion cycle, this liquid will tend to be at a lower temperatureand pressure than when sprayed into the gas undergoing or prior toexpansion, the liquid having imparted thermal energy to the gasundergoing expansion, and may be directed via the cylinder heat-exchangesystem 4304 to the cold thermal well 4334. Expanded gas at relativelylow temperature and pressure may be vented via vent 4305 to theenvironment from power unit 4302. Liquid will thus tend to betransferred from the high-temperature, high-pressure reservoir 4306 tothe cold thermal well 4334 during expansion cycles of the power unit4302.

The environmental heat exchangers 4332 and 4338 enable the temperaturesof the cold thermal well 4334 and the high-temperature, high-pressurereservoir 4306 to be managed in both expansion and compression modes asalready described hereinabove for thermal wells communicating withenvironmental heat exchangers. Heat from the waste-heat heat-exchangeunit 4310 may be transferred to the high-temperature, high-pressurereservoir 4306 via the waste-to-well heat-exchanger 4312. In otherembodiments, some or all of these heat exchangers are eliminated.

System 4300 may realize advantages already described hereinabove forsystems 3900, 4000, 4100, and 4200, including temperature management ofthe contents of the thermal well 4334 and of the high-temperature,high-pressure reservoir 4306, and partial conversion to work of wasteheat from power unit 4302. As with systems 4100 and 4200, it will beapparent to persons reasonably familiar with the principles ofthermodynamics that the maintenance of two bodies of liquid (i.e., inthe cold thermal well 4334 and in the high-temperature, high-pressurereservoir 4306) at (preferably) distinct temperatures decreases theentropy and increases the energy (extractable work) of system 4300,making the operation of system 4300 potentially more efficient than theoperation of a system (e.g., system 4000) having only a single thermalwell. Moreover, due to the elevation of the boiling point of water withincreasing pressure, system 4300 offers the additional advantage thatthe upper (non-vaporizing) temperature limit of water stored in thehigh-temperature, high-pressure reservoir 4306 is higher than the uppertemperature limit of water stored in a non-pressurized hot thermal wellsuch as hot thermal well 4208 of system 4200. It will be apparent topersons reasonably familiar with the principles of thermodynamics thatthe energy of a system increases when the temperature difference betweentwo bodies of liquid in the system is increased; thus, for example, theenergy of the bodies of hot and cold liquid of system 4300 may be higherthan the energy of similar quantities of hot and cold liquid in system4200, because the temperature difference between the bodies of hot andcold liquid in system 4300 may be, in some operating conditions ofsystem 4300, larger than the temperature difference between the bodiesof hot and cold liquid of system 4200.

FIG. 44 depicts an illustrative system 4400 that features a power unit4402 (including a cylinder assembly unit for compression and expansionof gas) that may include two or more different cylinder assemblies (thatmay have different diameters), each compressing or expanding gas over adifferent range of pressures (i.e., a two or more stage compressor andexpander power unit); a cylinder heat-exchange system 4404; a storagereservoir 4406 capable of holding both gas and liquid at high pressure(e.g., 3,000 psi) and relatively high temperature; a hot thermal well4408 including or consisting essentially of an insulated body of waterat low pressure (e.g., atmospheric pressure); a cold thermal well 4434also including or consisting essentially of a body of water; awaste-heat heat-exchange system 4410 coupled to waste heat generated bymechanical and electronic components of the power unit 4402; awaste-to-well heat-exchange system 4412 coupled on one side to the hotthermal well 4408 and on the other side to the waste-heat heat-exchangesystem 4410; a first environmental heat-exchange system 4432 capable ofexchanging thermal energy with the environment (e.g., the air, theground); and a second environmental heat-exchange system 4436 alsocapable of exchanging thermal energy with the environment (e.g., theair, the ground). The high-temperature, high-pressure reservoir 4406combines functions of a high-pressure gas store with functions of a hotthermal well.

Possible modes of operation of system 4400 include an expansion mode anda compression mode. In the compression mode, a quantity of gas (e.g.,air) at relatively low (e.g., atmospheric) pressure is admitted via vent4405 at an ambient or moderate temperature to the cylinder assembly ofpower unit 4402. As the cylinder assembly of power unit 4402 compressesthe gas, the compression is maintained substantially isothermal byintroduction into the gas of a spray of water drawn from the coldthermal well 4434 via the cylinder heat-exchange system 4404, therebyforming a foam within the cylinder assembly. The water thus sprayed intothe gas undergoing or prior to compression may be directed, along withthe compressed gas, via the cylinder heat-exchange system 4404 to thehigh-temperature, high-pressure reservoir 4406 at a higher pressure andtemperature than the water was drawn from cold thermal well 4434, havinggained thermal energy from the gas undergoing compression. Some or allspray water may also be directed to the low-pressure hot thermal well4408 via the cylinder heat-exchange system 4404. Water will thereforetend to be transferred from the cold thermal well 4434 to thehigh-temperature, high-pressure reservoir 4406 and/or low pressure hotthermal well 4408 during compression cycles of the power unit 4402.

Similarly, in the expansion mode of system 4400, a quantity of gas(e.g., air) at relatively high pressure (e.g., 3,000 psi) and relativelyhigh temperature is transferred from the high-temperature, high-pressurereservoir 4406 to the cylinder assembly of power unit 4402. As thecylinder assembly expands the gas, the expansion is maintainedsubstantially isothermal by introduction into the gas of a spray ofwater drawn from the high-temperature, high-pressure reservoir 4406 viathe cylinder heat-exchange system 4404, thereby forming a foam withinthe cylinder assembly. As the gas is expanded to lower pressures, thespray may be partially or even fully formed from water drawn from thelow-pressure hot thermal well 4408. The water sprayed through the gasundergoing or prior to expansion may be directed via the cylinderheat-exchange system 4404 to the cold thermal well 4434 at a relativelylow pressure and temperature, having imparted thermal energy to the gasundergoing expansion. Expanded gas may be vented to the environment viavent 4405 from power unit 4402. Water will thus tend to be transferredfrom the high-temperature, high-pressure reservoir 4406 and/orlow-pressure hot thermal well 4408 to the cold thermal well 4434 duringexpansion cycles of the power unit 4402.

The environmental heat exchangers 4436 and 4432 enable the temperaturesof the cold thermal well 4434 and low-pressure hot thermal well 4408 tobe managed in both expansion and compression modes, as already describedhereinabove for the thermal wells of systems 3900, 4000, 4100, 4200, and4300. Heat from the waste-heat heat-exchange unit 4410 may betransferred to the low-pressure hot thermal well 4408 via thewaste-to-well heat-exchange system 4412.

System 4400 may realize advantages already described hereinabove forsystems 3900, 4000, 4100, 4200, and 4300, including temperaturemanagement of the contents of the thermal wells 4408, 4434 and partialconversion to work of waste heat from power unit 4402. As with systems4100, 4200, and 4300, it will be apparent to persons reasonably familiarwith the principles of thermodynamics that the maintenance of two ormore bodies of liquid (i.e., in the cold thermal well 4434, in the hotthermal well 4408, and in the high-temperature, high-pressure reservoir4406) at (preferably) distinct temperatures decreases the entropy andincreases the energy (extractable work) of system 4400, making theoperation of system 4400 potentially more efficient than the operationof a system (e.g., system 400) having only a single thermal well. Due tothe elevation of the boiling point of water with increasing pressure,system 4400 offers (as does system 4300 in FIG. 43) the advantage thatthe upper (non-vaporizing) temperature limit of water stored in thehigh-temperature, high-pressure reservoir 4406 is higher than the uppertemperature limit of water stored in a non-pressurized hot thermal wellsuch as hot thermal well 4408. Moreover, system 4400 offers theadditional advantage that waste heat may be transferred from the powerunit 4402 to the low-pressure hot thermal well 4408 using a low-pressurewaste-to-well heat exchanger 4412, rather than a high-pressurewaste-to-well heat exchanger 4312 as in system 4300. A low-pressurewaste-to-well heat exchanger 4412 will tend to be less costly than ahigh-pressure waste-to-well heat exchanger.

Where power unit 4402 includes two different diameter cylinders (notdepicted), one (C1) compressing gas over a first, lower pressure range,and the second (C2) compressing gas over a second, higher pressurerange, advantages (e.g., increased overall efficiency of system 4400)may be realized in a compression mode of operation of system 4400 bymaintaining the low-pressure hot thermal well 4408 at a temperature (andoptionally also at the mid-pressure) achieved at the end of thesubstantially isothermal compression in C1. That is, low-pressure hotthermal well 4408 may be maintained at a lower temperature than thecontents of the high-pressure, high-temperature store 4406. This allowsthe quantity of spray introduced during or prior to compressions to beindependently adjusted in C1 and C2 as the pressure in the store 4406increases over sequential compression cycles. Further, if low-gradewaste heat (e.g., from a thermal power plant; not depicted) isavailable, it may be transferred via a heat exchanger to thelow-pressure, lower-temperature hot thermal well, increasing effectiveoverall system efficiency. The temperature of the low-pressure hotthermal well 4408 operating at a midpoint of a multi-stagecompression/expansion process may be optimal for usage of waste heat atavailable temperatures (e.g., approximately 40° C., 60° C., or similar),whereas the high-pressure high temperature reservoir 4406 may bemaintained at substantially higher temperature (e.g., approximately 80°C., 120° C. or similar) that may not allow usage of typical waste heattemperatures. By operating the multi-stage compression/expansion processat higher temperatures, reduced water spray volume may be used,increasing storage volume and system efficiency (e.g., reducing valvelosses for passing two-phase flow). It will be apparent to personsreasonably familiar with thermodynamics that similar advantages may berealized in an expansion mode of system 4400.

FIG. 45 depicts an illustrative embodiment of the invention in which oneor more batteries 4508 and/or other high-power, short-duration energystorage devices (e.g., an energy storage device with less than 1 hour ofstorage, e.g., 15 minutes) are connected in parallel with acompressed-gas energy storage system 4502 to generate power for usage(e.g., power grid delivery 4500). The energy storage system 4502 mayresemble illustrative storage systems depicted elsewhere herein. Thebattery 4508 is configured to provide stored energy during periods oflow power demand (e.g., less than 500 kW), while the compressed-gasenergy storage system 4502 is configured to provide stored energy duringperiods of increased power-demand fluctuations (e.g., above 500 kW). Inone example, the operator of a power generation facility that includes asolar power generation and the energy storage system depicted in FIG. 45receives payment to maintain a constant power level of 2,000 kW. At aninstant, solar power generation drops from 2,000 kW to 1,900 kW as acloud shadows part of the array. Measured power output may be maintainedat the required constant power level by requiring that the battery 4508discharge at a rate of 0 to 100 kW as the cloud shadows the array. Atanother instant, a storm passes the area and the solar power generationdrops to 1000 kW to 500 kW for an extended period of time. Measuredpower output may be maintained at the constant power level by requiringthat the compressed-gas energy storage system 4502 discharges at a rateof 1000 to 1500 kW as the cloud shadows the array. Upon demand forincreased power (e.g., above 500 kW), stored energy in the form ofcompressed gas in storage reservoir 4504 undergoes expansion in thecompressed-gas energy storage system 4502 to generate power for usage(e.g., power grid delivery 4500). Any excess thermal energy from thebattery 4508 may be recoverable through a heat-exchange unit 4506. Therecovered thermal energy from the battery 4508 may be used in theheat-exchange subsystem of the compressed-gas storage reservoir 4504 (orother pressurized storage) to preheat the stored compressed gas and/orto heat the heat-exchange fluid and gas during expansion, increasing thework done by a given volume of pressurized gas, and so improving systemefficiency and/or performance. For example, the recovered thermal energymay be utilized to thermally condition stored compressed gas and/or gasundergoing expansion and/or compression as described in the '960application.

The response time of the high-power, short-duration energy storagedevice 4508 may be optimized to respond within microseconds to changingpower levels and demand. The rate of the power response may be limitedto approximately one millisecond based on the data acquisition rate ofthe control system, but can readily be configured to respond in lessthan one second.

FIG. 46 depicts an integrated system 4600 in which a compressed-gasenergy storage system 4610 including one or more storage reservoirs withstored compressed gas (not depicted) is connected to an electric motor4612. During periods of higher power demand fluctuations (e.g., above500 kW) the compressed-gas energy storage system 4610 is discharged toprovide motor 4612 with stored energy. The motor 4612 converts thestored energy into electric power. In some embodiments, for asynchronous electric machine running at synchronous speeds (e.g., 1800RPM), no power electronics are required. In other embodiments, for avariable-speed electric machine, as illustrated in FIG. 46, electricpower is sent to load-side power electronics 4608 that convert theelectric current from AC to DC before sending the power through a commonDC bus line 4606. Electric power may then be sent to line-side powerelectronics 4604 (DC to AC) for usage (e.g., by power grid 4602). Duringperiods of low power-demand fluctuations (e.g., less than 500 kW) one ormore batteries 4650, and/or other high-power, short-duration energystorage devices (e.g., flywheels and/or ultracapacitors), are dischargedto provide power for usage. For a DC device such as a battery, theelectrical output may be connected to the same line-side powerelectronics. For example, electric power may be discharged from thebattery 4650 through the common DC bus line 4606 to line-side powerelectronics 4604 before being sent for usage (e.g., power grid 4602).

In various embodiments, the battery 4650 is connected to a coolingsystem featuring a heat exchanger 4648, a radiator 4634, a battery inletpipe 4632 with a pump 4630, a fluid control valve 4628, and a batteryreturn pipe 4638 with a fluid control valve 4636. Similarly, thecompressed-gas energy storage system 4610 is connected to aheat-exchange subsystem featuring a heat exchanger 4614, a radiator4620, an inlet pipe 4622 with a pump 4616, a fluid control valve 4618,and a return pipe 4626 with a fluid control valve 4624. Radiator 4620may alternatively or additionally include or consist essentially of athermal well. The battery inlet pipe 4632 may be connected to the inletpipe 4622 via pipe 4642. Likewise, the battery return pipe 4638 may beconnected to the return pipe 4626 via pipe 4640. Pipes 4642 and 4640 maycontain fluid control valves 4644 and 4646 respectively.

In a state of operation in which the compressed-gas energy storagesystem 4610 is discharged to provide power to the grid (e.g., demandexceeds supply by more than 500 kW), valve 4628 is closed and valve 4644is opened to allow heat-transfer fluid from battery inlet pipe 4632 tobe sent to inlet pipe 4622 via pipe 4642. Heat-transfer fluid iscirculated via pump 4616 through heat exchanger 4614, return pipe 4626,and radiator 4620. During circulation in the heat-exchange subsystem,waste heat from the battery 4650 cooling system is used to heat thecompressed gas prior to and/or during expansion in the compressed-gasstorage system 4610 (e.g., by formation of foam between the gas and theheated heat-transfer fluid). The storage system 4610 power density isthereby increased and/or overall efficiency is improved.

In a different state of operation in which the battery 4650 isdischarged to provide power to the grid (e.g., demand exceeds supply byless than 500 kW), valve 4644 and 4646 are closed and heat exchanger4648, battery inlet pipe 4622, pump 4630, radiator 4634, and batteryreturn pipe 4638, form a closed-loop battery-cooling system independentof the heat-exchange subsystem of the compressed-gas energy storagesystem 4610. In other modes of operation, waste heat from the battery4650 may be directed to the thermal well 4620 where the thermal energymay be stored to be used at a later time during operation of thecompressed-gas storage system 4610.

FIG. 47 is an illustrative plot of electricity supply and demand for anexemplary 24-hour period. The supply curve is based on a simulation of asource of constant-baseload power and an exemplary solar installation,whereas electricity demand is based on simulated data from an exemplaryday. Electricity demand is typically lower during the evening and higherduring the day. In the illustrative plot shown in FIG. 47, demandexceeds supply from approximately hour 15 (900 minutes) to hour 24 (1440minutes).

FIG. 48 is an illustrative plot of the effect of a combined high-power,short-duration energy storage device and compressed-gas energy storagesystem on electricity supply and demand for a given 24-hour period. Inthe illustrative plot shown in FIG. 48, at minute zero demand exceededsupply by around 200 kW. The high-power, short-duration energy storagedevice is configured to discharge power to meet excess demand valuesless than 500 kW. Therefore, the high-power, short-duration energystorage device is shown in a discharging state from minute zero tominute 60 where the range of excess demand is 200 kW to 0 kWrespectively. From minute 60 to minute 120, supply exceeds demand byless than 500 kW. Therefore, the high-power energy-storage device isshown in a charging state (depicted as negative values in FIG. 48) untilthe maximum power is reached at −500 kW.

The compressed-gas energy storage system is configured to dischargepower to meet excess demand values above 500 kW. (In one embodiment,multiple 1 MW systems act as a larger system to address any power above500 kW by employing multiple power units, e.g., two 1 MW systems mayaddress power levels between 500 and 2000 kW). In the illustrative plotshown in FIG. 47, when supply exceeds demand in the range of 500 kW ormore, the excess power is used to charge the compressed-gas energystorage system (i.e., store energy in the form of compressed gas).Therefore, the compressed-gas storage system is shown in a chargingstate from minute 120 to minute 540 when the excess power falls below500 kW (depicted as negative values in FIG. 48). When the excess powerfalls below 500 kW, the high-power energy-storage device takes over andis therefore shown in a charging state (depicted as negative values inFIG. 48) from minute 540 to minute 600.

During the period ranging from minute 600 to minute 900, supply exceedsdemand by varying values less than 500 kW; therefore, the high-power,short-duration energy storage device is shown in a charging state whenvalues are less than 500 kW. Additionally, to maintain thestate-of-charge of the high-power, short-duration energy storage devicewithin a certain range, the compressed-gas energy storage device isshown in a charging state at −500 kW whenever the state-of-charge of thehigh power, short duration energy storage device exceeds a set maximumvalue (e.g., 900 kWh, as shown in FIG. 48 or in a discharging state at500 kW whenever the state-of-charge of the high-power, short-durationenergy storage device drops below a set minimum value (e.g., 100 kWh, asshown in FIG. 48). When demand exceeds supply from minute 900 to minute1440, the high-power, short-duration energy storage device is dischargedfor the first 500 kW demand period. Afterwards, the compressed-gasenergy storage system takes over and discharges power for the periodwhere demand exceeds supply by 500 kW or more.

FIG. 49 is an illustrative plot of the state-of-charge for the combinedhigh-power, short-duration energy storage device and compressed-gasenergy storage system for the given 24-hour period illustrated in FIGS.47 and 48. In this simulated scenario, a 2 MW compressed-gas energystorage system with 10 MWh of storage capacity operates in parallel witha 500 kW short-duration energy-storage device with storage capacity upto 1 MWh. Whenever the state-of-charge of the high-power, short-durationenergy storage device exceeds 900 kWh (90% of maximum capacity), aportion of the stored energy is discharged to either the grid or to thecompressed-gas energy storage system. Whenever the state-of-charge ofthe high-power, short-duration energy storage device drops below 100 kWh(10% of maximum capacity), the high-power, short-duration energy storagedevice is recharged via either the grid or the compressed-gas energystorage system. In this manner, the state-of-charge of the high-power,short-duration energy storage device may be maintained within an optimalrange while the compressed gas energy storage system provides bulkenergy storage and recovery.

Embodiments of the invention may be applied in a wide variety ofsettings where generation assets are connected to a grid whose loads mayvary over time (e.g., with time of day), and where the power output ofsome generation assets may vary (e.g., with wind conditions, cloudconditions, mechanical breakdowns, transmission line failures, closuresfor scheduled refueling of a reactor core). Some of these applicationsare discussed further below.

Embodiments of the invention may also be applied in a variety of “behindthe meter” settings, i.e., where a power user's access to power, or costof power, varies over time (e.g., with time of day) and it isadvantageous for the user to buy and store energy using a compressed-airenergy storage system at some times and to generate power using thestorage system at other times.

FIG. 50 is a conceptual drawing of an illustrative power generation andconsumption network or grid 5000 of conventional baseload power plants5002, very-high-voltage transmission lines 5004, transmissionsubstations 5006, regional high-voltage transmission lines 5008, largepower loads 5010 with their own step-down transformers 5012, centralizedrenewable power generators 5014 (e.g., solar panels, wind turbines)connected by transmission lines 5015 to the network at, e.g.,substations 5006, area transmission lines 5018, distribution substations5020, local distribution lines 5022, small-scale power loads 5024 (e.g.,homes), and isothermal compressed-air storage (ICAES™) systems 5026,5028, 5030, 5032, 5034 that may exchange energy with other components ofthe network 5000 at a variety of points (as indicated by double-headedarrows). Such ICAES systems may include or consist essentially of anyone or more of the illustrative energy storage systems describedelsewhere herein, including those which employ foam-based heat transferto increase thermal efficiency and speed (hence power density) ofoperation of cylinder assemblies.

Single representations of power lines, substations, loads, and ICAESsystems stand, in the conceptual drawing of FIG. 50, for a possiblemultiplicity of complexly interconnected units of the same types: thatis, network 5000 is a simplified representation of components of a classof real-world networks (power grids) that may be far more complex thannetwork 5000 as represented in FIG. 50 and that may contain components(e.g., peak generators fired by natural gas) not represented in FIG. 50.Nevertheless, relationships indicated by FIG. 50 may accuratelyrepresent relationships between components in more complex real-worldnetworks.

Applications of ICAES in network 5000 may be classed into at least fourmajor categories, (1) conventional power generation, (2) renewable powergeneration and cogeneration, (3) transmission and network services, and(4) end user support.

Conventional Power Generation

Where ICAES 5026 is connected to the low-voltage side of the step-uptransformer system at a conventional power plant 5002, several functionsmay be performed by the ICAES 5026. The operation of the ICAES 5026 andof its electrical connection with the low-voltage (local) electricalsystem of the power plant 5002 is governed by a control system (notdepicted) including or consisting essentially of automatic controls(e.g., digital computers), human controllers, or both. Signals derivedfrom a variety of sources may be directed to the control system of ICAES5026. Such signals include measured, electronically coded, and remotelytransmitted (reported) information describing the availability andoutput of other generation sources (both conventional 5002 and renewable5014) attached to the network 500, the magnitude and location of loads(e.g., 5010, 5024), recent changes in the availability and output ofgenerators of all types throughout network 5000 (including generatorsnot represented in FIG. 50, e.g., rooftop solar panels co-located withloads 5010, 5024 in a geographically distributed manner), recent changesin magnitudes of loads 5010, 5024, quantitative estimates of energystored in ICAES systems and other storage systems (e.g., hydroelectricstorage reservoirs), quantitative forecasts (from, e.g., the NationalWeather Service) of temperatures and other aspects of weather in areaswhere loads are located, forecasts of renewable (e.g., hydroelectric)generation capacity based on recent weather events (e.g., precipitation)over geographically relevant areas, instantaneous market prices forexchange of power between network 5000 and other networks, impendingphysical challenges to the network 5000 (e.g., storms), operationalstatus and loading of transmission facilities 5004, etc.

The controller bases decisions about the operation of ICAES 5026 uponthe signals it receives. For example, energy from the conventionalgenerator 5002 (or from elsewhere in the network 5000 via transmissionlines 5004) may be stored in ICAES 5026 at a time when there is asurplus of generating capacity relative to load (e.g., at night). Atsuch times as there is a shortage of generating capacity relative todemand (e.g., during peak demand near mid-day), or when more-expensivegenerators (e.g., gas-fired peak generators) would necessarily be calledinto action to meet demand, energy may be retrieved from ICAES 5026 andtransmitted to loads through network 5000. Such electric energytime-shifting may decrease energy costs in network 5000 by obviating ormitigating the operation of more-expensive peak generators.

Alternatively or additionally, the ICAES 5026 associated with aparticular generator may act as reserve capacity from which energy maybe extracted when one or more other generators (not depicted) in network5000 become unavailable (e.g., due to mechanical failure or scheduledrefueling) or must operate at reduced capacity (e.g., due to low waterlevels at a hydroelectric facility).

Alternatively or additionally, energy may be extracted from ICAES 5026in response to increases in loads 5024, 5010 throughout network 5000.Such increases in load may be routine (e.g., the daily peak in demand)or unusual (e.g., due to statistical fluctuations in large numbers ofsmaller loads, or due to a large user 5010 coming on line). Suchapplications may generally be termed a form of “load following.”

Renewable Power Generation

ICAES 5028, co-located with renewable generators 5014 of significantsize (i.e., wind farms or other non-distributed generators), canincrease the value of the power provided by such generators by reducingthe intermittency of their power output as seen by a purchaser of thatoutput through the transmission lines 5015. That is, during periods whendemand for power is low or generation by the renewable generator 5014 isrelatively high, some or all energy produced by the renewable generator5014 may be stored in ICAES 5028. At periods when demand (and/or price)for power is higher or when generation by the renewable generator 5014is relatively low, energy may retrieved from ICAES 5028 and transmittedto the network 5000 via power lines 5015. Retrieval of energy from ICAES5028 on a regular schedule is generally termed energy time-shifting; useof ICAES 5028 to mitigate the output intermittency of the generator 5014is generally termed firming of the generator. In many real-worldnetworks, the per-unit value of energy from a given generator is partlyconditioned on the on-demand availability of that energy: since theavailability of a unity of energy from a renewable generator 5014 isincreased by the partial buffering of the output of generator 5014through ICAES 5028, the use of ICAES 5028 to firm the output ofrenewable generator 5014 may be advantageous.

Transmission and Network Services

By means of appropriate electronic control signals, the controller ofICAES 5026 may simultaneously or independently control ICAES units 5026,5028, 5030, 5032, 5034 and other energy-storage systems that may belocated throughout the network 5000. ICAES units may be attached tonetwork 5000 at some or all of the points indicated in FIG. 50, and/orat additional points not depicted in FIG. 50. Simultaneousremote-control operation of ICAES units and other storage unitsthroughout network 5000 may provide a variety of transmission andnetwork services, for example, enable the lowest-cost matching ofgenerators (including storage units) to loads throughout the network atall times, or, if total load should exceed the generating capacity ofnetwork 5000, the minimization of economic and other losses due tosupply-demand mismatch. Short-term fluctuations in load 5024, 5010,which may cause voltages on transmission lines to drop throughoutportions of network 5000, may be mitigated by the rapid activation ofICAES units (e.g., units 5034, 5030) to add energy to network 5000. Suchactivation of rapid-response generators may generally be termed voltagesupport.

At times when some transmission lines (e.g., 5018) are heavily loaded,i.e., are carrying as much, or nearly as much, power as they are safelycapable of carrying, yet demand increases (e.g., at load 5024), thecontroller may cause energy to be extracted from storage (e.g., ICAES5034) in order to obviate the need for the transmission of additionalpower through the heavily loaded transmission line. Such transmissionsupport may allow scheduled upgrades of the capacity of certaintransmission lines in network 5000 to be deferred. Relief of temporarytransmission congestion may also be afforded by such means.

Power to individual substations (e.g., 5006, 5020) may be supplied byICAES units attached thereto (e.g., 5030, 5034) during widespread poweroutages, supporting on-site operations and thus speedier networkrecovery.

End User

Energy stored at ICAES units distributed in the grid (e.g., 5032, 5034)may be used to temporarily supply power to local loads whenlong-distance transmission lines (e.g., 5004, 5008) are disabled oroverloaded, or when primary generators (e.g., 5002) are disabled, or inother outage conditions. Such powering of a local network of loads isgenerally termed islanding. Islanding of residential neighborhoods,industrial parks, large buildings, military bases, large single users(e.g., 5010), and other local loads may be enabled or supported by ICAESunits.

Time-of-use management for single large users 5010 may be enabled byICAES 5032. That is, energy may be purchased by the user 5010 from thegrid when prices are lower (e.g., at night), stored in ICAES 5032, thenextracted from storage when prices are higher (e.g., during the day).Additionally or alternatively, ICAES 5032 may assure power quality ishigh to the user 5010, protecting against economic losses (e.g., datalosses) entailed by fluctuations in quality or availability of powerfrom the network 5000. Additionally or alternatively, storage of energyin and retrieval of energy from ICAES 5032 may enable user 5010 to shapeits demand profile in a way that manages demand charges and time-of-use.

All these applications of the invention, as well as others notexplicitly described herein, are contemplated.

Generally, the systems described herein may be operated in both anexpansion mode and in the reverse compression mode as part of afull-cycle energy storage system with high efficiency. For example, thesystems may be operated as both compressor and expander, storingelectricity in the form of the potential energy of compressed gas andproducing electricity from the potential energy of compressed gas.Alternatively, the systems may be operated independently as compressorsor expanders.

Embodiments of the invention may, during operation, convert energystored in the form of compressed gas and/or recovered from the expansionof compressed gas into gravitational potential energy, e.g., of a raisedmass, as described in U.S. patent application Ser. No. 13/221,563, filedAug. 30, 2011, the entire disclosure of which is incorporated herein byreference.

Systems in accordance with embodiments of the invention may utilize asubstantially incompressible fluid and/or one or more pressurizedreservoirs to minimize or eliminate dead space within one or morecylinder assemblies and/or other components, as described in the '914application and in U.S. patent application Ser. No. 13/080,910, filedApr. 6, 2011, the entire disclosure of which is incorporated herein byreference. As also described in these applications, embodiments of theinvention may incorporate mechanisms for substantially preventing theflow of compressible fluid (e.g., gas or foam) from the cylinderassembly into the heat-exchange components (e.g., heat exchangers,pumps, and/or pipes connected thereto and/or between the cylinderassembly and such components), and may thereby substantially preventformation of dead space in the heat-exchange components. For example,various embodiments incorporate one or more check valves on the upstreamside of one or more of the nozzles in the spray-generating orfoam-generating mechanism introducing heat-exchange fluid into acylinder assembly.

The terms and expressions employed herein are used as terms ofdescription and not of limitation, and there is no intention, in the useof such terms and expressions, of excluding any equivalents of thefeatures shown and described or portions thereof, but it is recognizedthat various modifications are possible within the scope of theinvention claimed.

What is claimed is: 1.-44. (canceled)
 45. An energy storage and recoverysystem comprising: a cylinder assembly for at least one of storingenergy by compression or recovering energy by expansion; a storagereservoir; and selectively fluidly connected to the cylinder assemblyand the storage reservoir, a mixing chamber for (i) receiving gas andheat-transfer liquid from the storage reservoir, (ii) mixing the gaswith the heat-transfer liquid to form a foam, and (iii) transferring thefoam to the cylinder assembly, wherein the mixing chamber is selectivelyfluidly connected to the storage reservoir by (i) a first conduit fortransferring gas and (ii) a second conduit, different from the firstconduit, for transferring heat-transfer liquid.
 46. The system of claim45, further comprising, within the mixing chamber, a mechanism foraltering at least one characteristic of the foam.
 47. The system ofclaim 46, wherein the mechanism comprises at least one of a screen or asource of ultrasound energy.
 48. The system of claim 46, wherein the atleast one characteristic comprises at least one of foam cell size orfoam cell size uniformity.
 49. The system of claim 45, furthercomprising, coupled to at least one of the first conduit or the secondconduit in the mixing chamber, a foam-generating mechanism.
 50. Thesystem of claim 49, wherein the foam-generating mechanism comprises atleast one of one or more nozzles, a rotating blade, a source ofultrasound energy, or a sparger.
 51. The system of claim 45, furthercomprising a second cylinder assembly for at least one of storing energyby compression or recovering energy by expansion over a pressure rangedifferent from a pressure range of the cylinder assembly.
 52. The systemof claim 51, further comprising, selectively fluidly connected to thesecond cylinder assembly, a vent for exhausting expanded gas toatmosphere.
 53. The system of claim 45, further comprising a controlsystem for controlling at least one of the cylinder assembly or themixing chamber to enforce at least one of substantially isothermalcompression or substantially isothermal expansion in the cylinderassembly.
 54. The system of claim 53, further comprising a sensor fordetecting a pressure within at least one of the cylinder assembly or themixing chamber, wherein the control system is responsive to the sensor.55. The system of claim 54, wherein the control system controls a flowrate of heat-transfer liquid into the mixing chamber in response to thedetected pressure.
 56. The system of claim 45, further comprising acirculation apparatus for transferring heat-transfer liquid within thesecond conduit.
 57. The system of claim 56, wherein the circulationapparatus comprises a variable-speed pump.
 58. The system of claim 45,further comprising: (i) a movable boundary mechanism separating thecylinder assembly into two chambers, and (ii) a crankshaft, mechanicallycoupled to the boundary mechanism, for converting reciprocal motion ofthe boundary mechanism into rotary motion.
 59. The system of claim 58,further comprising a motor/generator coupled to the crankshaft.
 60. Thesystem of claim 45, wherein the storage reservoir comprises at least oneof a pressure vessel, a pipe, or a cavern.
 61. The system of claim 45,wherein the first conduit also transfers liquid.
 62. The system of claim45, wherein the second conduit also transfers gas. 63.-451. (canceled)